Reciprocating rotation opposed linear piston engine power device and power assembly

Abstract

The invention belongs to the technical field of power equipment, and discloses a reciprocating rotation opposed linear piston engine power device and a power assembly. The device comprises a machine body, a cylinder cover, a piston, a cylinder, a rotary cylinder, a roller body, a longitudinal push rod, a transverse push rod, a first power shaft, a second power shaft and a flywheel, the four cylinders are arranged on the two sides of the rotary column body in a pairwise opposite mode, and the middle section of the rotary column body is provided with a wavy double-V-shaped groove and an open groove which are connected end to end. The roller body is provided with a central bearing and a double-frustum surface, and the double-frustum surface is matched with the groove, is arranged at an interval and rolls along the groove; the longitudinal push rod is connected with the two pistons on the same side and axially parallel to the rotary cylinder, the transverse push rod is perpendicularly connected with the longitudinal push rod and penetrates through the open groove to be fixed to the center bearing, and the roller body can rotate around the transverse push rod. Two ends of the rotary cylinder are respectively connected with a first power shaft and a second power shaft, the first power shaft is connected with a flywheel to form a first power output end, and the second power shaft is a second power output end. Parts and friction pairs are reduced, the cost is reduced, and the specific power is improved.

Description

Technical Field

[0001] This application belongs to the field of power equipment technology, specifically relating to a reciprocating rotary opposed linear piston engine power unit and power assembly. Background Technology

[0002] Piston engines, as the core component of power output, are widely used in automobiles, construction machinery, range extender systems for new energy vehicles, and many other fields. Most existing engines convert the reciprocating motion of the piston into rotational motion through a crankshaft connecting rod mechanism. This transmission structure has inherent mechanical losses, resulting in low power output efficiency. It is difficult to balance power performance and speed flexibility, and cannot meet the differentiated requirements of speed and power for different application scenarios.

[0003] Existing engines are mostly customized designs, adapted to single application scenarios, and cannot flexibly meet the needs of different fields such as new energy vehicle range extenders, traditional vehicles, and construction machinery. When adapted to new energy vehicle range extenders, it is difficult to meet the dual needs of high-voltage power supply for the drive motor and low-voltage power supply for on-board electrical appliances, resulting in low range extension efficiency and failure to effectively extend vehicle range. When adapted to traditional vehicles, the engine and transmission have poor compatibility, resulting in unstable power transmission, easy power interruption during gear shifts, and the need to add an additional generator to meet the power supply needs of on-board electrical appliances, increasing system complexity. When adapted to construction machinery, it cannot effectively buffer load impacts, and is prone to engine overload damage under heavy-load start-up and frequent reversing scenarios. It is also difficult to simultaneously meet the power supply needs of operating power and auxiliary equipment, resulting in extremely poor compatibility. Summary of the Invention

[0004] The technical problem to be solved by this application is to overcome the shortcomings of the prior art and provide a reciprocating rotary opposed linear piston engine power unit and power assembly. This application effectively reduces the number of engine parts, reduces mass and friction pairs, lowers engine cost, and increases engine specific power.

[0005] The technical solution adopted in this application to solve the problems existing in the prior art is: A reciprocating rotary opposed linear piston engine power unit includes a body, two or more pairs of opposing cylinders, wherein each pair of opposing cylinders is symmetrically arranged along the circumference and axial direction of the body, each cylinder is provided with a piston, and each cylinder is provided with a cylinder head at the top.

[0006] It also includes a rotating cylinder, multiple rollers, multiple longitudinal push rods, and multiple transverse push rods.

[0007] The rotating cylinder is located at the center of the machine body in both the axial and circumferential directions, and is fixedly supported on it by bearings. The axis of the rotating cylinder is parallel to the axis of each pair of opposing cylinders.

[0008] The middle section of the rotating cylinder is provided with a wavy double V-shaped groove along the circumference of the cylinder. The two V-shaped grooves of the wavy double V-shaped groove are located at the two ends of the axial direction, and the beginning and end of the wavy double V-shaped groove are connected. The middle of the wavy double V-shaped groove is provided with an opening groove facing the cylindrical surface.

[0009] The wavy double V-shaped groove contains several roller bodies, each with a central bearing at its center. The outer circumferential surface of each roller body is a double-conical truncated cone, wider in the middle and narrower at both ends. The included angle of the generatrix of the double-conical frustum of the roller body is equal to the V-groove angle of the wavy double V-groove, and the double-conical frustum of the roller body is arranged with a gap between the double V-groove surface of the wavy double V-groove, and the roller body rolls along the wavy double V-groove.

[0010] The longitudinal centerline of each longitudinal push rod is parallel to the axial centerline of the rotating cylinder. Each end of each longitudinal push rod is connected to a piston.

[0011] One end of each transverse push rod is fixedly connected to the middle of one of the longitudinal push rods, and the axis of the transverse push rod is perpendicular to the axis of the longitudinal push rod. The other end of each transverse push rod passes through an opening slot and is fixedly connected to the center bearing hole of the central bearing, and the roller body rotates around the axis of the transverse push rod.

[0012] The two ends of the rotating cylinder are coaxially connected to a first power shaft and a second power shaft, respectively. The end of the first power shaft away from the rotating cylinder is fixedly connected to one end of the flywheel. The other end of the flywheel is the first power output end, and the end of the second power shaft away from the rotating cylinder is the second power output end.

[0013] Furthermore, the distance from the longitudinal centerline of each longitudinal push rod to the axial centerline of the rotating cylinder is equal.

[0014] Furthermore, the wave height between the crests and troughs of the axial centerline of the wavy double V-shaped groove of the rotating cylinder is equal to the stroke of each piston.

[0015] Furthermore, the number of crests and troughs of the wavy double V-shaped groove of the rotating cylinder are equal, and the number of crests is equal to the number of cylinders, or the number of crests is an integer multiple of the number of cylinders, or the number of crests is half the number of cylinders.

[0016] Furthermore, the cylinder head is equipped with electronic intake valves, electronic exhaust valves, spark plugs, and a combustion chamber.

[0017] Furthermore, the cylinder head is equipped with electronic intake valves, electronic exhaust valves, high-pressure fuel injectors, and a combustion chamber.

[0018] A powertrain based on the aforementioned reciprocating rotary opposed linear piston engine power unit, wherein the first power output end of the flywheel is connected to the power input end of a high-voltage generator, and the second power output end of the second power shaft is connected to the power input end of a low-voltage generator, forming a powertrain adapted for the application of range extenders in new energy vehicles.

[0019] A powertrain based on the aforementioned reciprocating rotary opposed linear piston engine power unit, wherein the first power output end of the flywheel is connected to the power input end of an automatic transmission, and the second power output end of the second power shaft is connected to the power input end of a low-voltage generator, forming a powertrain adapted to conventional automotive applications.

[0020] A powertrain based on the aforementioned reciprocating rotary opposed linear piston engine power unit, wherein the first power output end of the flywheel is connected to the power input end of the hydraulic torque converter, and the second power output end of the second power shaft is connected to the power input end of the low-voltage generator, forming a powertrain adapted to engineering machinery applications.

[0021] Compared with the prior art, the beneficial effects of this application are as follows: (1) The structure adopts a four-cylinder opposed installation, with two cylinders sharing a set of longitudinal and transverse push rods. Combined with the matching design of double-cone pedigree roller body and wave-shaped double V-groove, the transverse thrust borne by the transverse push rod can be decomposed, reducing the stress concentration of the push rod, solving the problem of rapid wear and stress imbalance of components in the power transmission process of existing engines, and extending the service life of core components. A small lubrication gap is set between the roller body and the groove to take into account the stability of contact transmission and the anti-jamming effect, avoiding the problem of large friction loss and power transmission interruption in the existing transmission structure, and improving the continuity of power transmission.

[0022] The rotating cylinder is fixedly supported by rolling bearings at both ends. Combined with the opposed cylinder layout, it effectively balances the cylinder pressure and vibration during engine operation, reduces operating noise, and significantly improves the smoothness of operation compared to traditional crankshaft connecting rod engines, making it suitable for high and low load switching scenarios.

[0023] (2) Through the coordinated operation of longitudinal push rod, transverse push rod, roller body and rotating cylinder, the reciprocating motion of piston is efficiently converted into the rotational motion of rotating cylinder, the power loss is lower than that of traditional crankshaft connecting rod structure, and the power output efficiency is higher.

[0024] The reduction ratio can be flexibly adjusted by changing the number of crests in the wave-shaped double V-groove to adapt to different speed requirements, thus solving the limitation of the single speed adaptability of existing engines and balancing power performance and speed flexibility.

[0025] (3) Adaptable to both spark and compression ignition combustion modes: Spark ignition optimizes the valve timing and ignition rhythm through precise coordination of electronic intake valve, electronic exhaust valve and spark plug, solving the problems of incomplete combustion and large power fluctuations in traditional spark ignition engines, improving fuel utilization and reducing exhaust emissions; Compression ignition achieves fine fuel atomization through high-pressure injectors, combined with precise valve timing, reducing fuel consumption and carbon deposit generation, adapting to the high-efficiency requirements of heavy-duty power scenarios.

[0026] (4) It can be specifically adapted to three major scenarios: new energy vehicle range extenders, traditional vehicles, and construction machinery. Through the flexible connection between the power output end and high-voltage generators, low-voltage generators, automatic transmissions, and hydraulic torque converters, it solves the problem of poor adaptability of existing engine scenarios and difficulty in balancing power and power supply: when adapted to new energy vehicles, it improves range extension efficiency and extends range; when adapted to traditional vehicles, it optimizes driving smoothness and simplifies the power system; when adapted to construction machinery, it buffers load impact and improves adaptability to complex working conditions.

[0027] (5) The integrated structure design of the opposing cylinders sharing the push rod and the dual power output simplifies the overall structure of the power system, reduces the space occupied by the vehicle body or equipment, and is suitable for the compact structure requirements of new energy vehicles, construction machinery and other industries. Attached Figure Description

[0028] The present application will be further described below with reference to the accompanying drawings and embodiments.

[0029] Figure 1 This is a schematic diagram of the structure of the present invention adapted for use in range extenders for new energy vehicles.

[0030] Figure 2 This is a schematic diagram of the structure of the present invention adapted for use in traditional automotive power units.

[0031] Figure 3 This is a structural schematic diagram of the present invention adapted for use in engineering machinery power devices.

[0032] Figure 4 This is a schematic diagram illustrating the basic working principle of the rotating cylinder, roller, longitudinal push rod, and transverse push rod of the present invention, which achieve reciprocating rotation during the power stroke of each cylinder in the engine.

[0033] Figure 5 This invention provides a schematic diagram illustrating the basic working principle of the rotating cylinder, roller, longitudinal push rod, and transverse push rod reciprocating during the intake stroke of each cylinder in an engine.

[0034] In the diagram: 1-Cylinder head, 1a-Electronic exhaust valve, 1b-Electronic intake valve, 1c-Spark plug, 1d-High-pressure fuel injector, 2-Piston, 3-Cylinder, 4-Longitudinal pushrod, 5-Transverse pushrod, 6-Roller body, 6a-Central bearing, 6b-Double cone pedestal, 7-Roller body, 7a-Wave double V-groove, 7b-Open slot, 8-First power shaft, 9-Second power shaft, 9a-Second power output end, 10-Main body, 11-Rolling bearing, 12-Speed ​​and piston top dead center position sensor, 13-Flywheel, 13a-First power output end, 14-Starter, 15-Low-voltage generator, 16-High-voltage generator, 17-Automatic transmission, 18-Torque converter. Detailed Implementation

[0035] The present application provides a detailed description of a reciprocating rotary opposed linear piston engine power unit and powertrain in conjunction with the accompanying drawings, but this is not intended to limit the scope of the application.

[0036] Depend on Figures 1 to 5 As shown, a reciprocating rotary opposed linear piston engine power unit has four cylinders, namely cylinder I, cylinder II, cylinder III, and cylinder IV.

[0037] Cylinder I and Cylinder II are mounted opposite each other, and these two cylinders share a longitudinal push rod 4 and a transverse push rod 5. Cylinder III and Cylinder IV are mounted opposite each other, and these two cylinders share a longitudinal push rod 4 and a transverse push rod 5. That is, the whole device has two longitudinal push rods 4 and two transverse push rods 5.

[0038] The axis of the transverse push rod 5 forms a 90° angle with the axis of the longitudinal push rod 4. The longitudinal push rod 4 is arranged along the cylinder axis, and the transverse push rod 5 is arranged perpendicular to the longitudinal push rod.

[0039] The power unit of the reciprocating rotary opposed linear piston engine also includes a rotating cylinder 7 and two rollers 6.

[0040] The rotating cylinder 7 has a wavy double V-shaped groove 7a along its circumference in the middle section. The two V-shaped grooves of the wavy double V-shaped groove 7a are located at opposite ends of the axial direction of the rotating cylinder 7 and are symmetrically distributed. The wavy double V-shaped groove 7a are connected end to end to form a closed groove structure. The wavy double V-shaped groove 7a has an opening groove 7b in the middle facing the cylindrical surface. The opening groove 7b extends along the circumference of the rotating cylinder 7 to allow the transverse push rod 5 to pass through and to reserve space for movement.

[0041] Each roller body 6 has a central bearing 6a at its center. The inner ring of the central bearing 6a is fixedly connected to the transverse push rod 5, and the outer ring is rigidly fixed to the roller body 6. The circumferential outer surface of each roller body 6 is a double-conical frustum 6b, which is larger in the middle and smaller at both ends.

[0042] The generatrix angle α6 of the double-conical frustum surface 6b of each roller body 6 is equal to the V-groove angle α7 of the double V-groove of the wavy double V-groove 7a. Furthermore, the double-conical frustum surface 6b of each roller body 6 and the double V-groove surface of the wavy double V-groove 7a maintain a slight lubrication gap, which ensures the stability of the contact transmission and avoids friction jamming.

[0043] Each roller body 6 is embedded in the wavy double V-shaped groove 7a of the rotating column 7, and each roller body 6 is evenly distributed along the circumference of the rotating column 7. Two roller bodies 6 correspond to two transverse push rods 5 and are symmetrically arranged on both sides of the rotating column 7. Each roller body 6 can roll along the wavy double V-shaped groove 7a and perform compound motion with the groove contour.

[0044] The longitudinal centerline of each longitudinal push rod 4 is parallel to the axial centerline of the rotating cylinder 7, and the distance from the longitudinal centerline of each longitudinal push rod 4 to the axial centerline of the rotating cylinder 7 is equal. Each end of each longitudinal push rod 4 is connected to a piston 2, and the pistons 2 at both ends of each longitudinal push rod 4 are installed in line opposite each other in each cylinder 3 to ensure that the reciprocating motion of the piston can be synchronously transmitted to the longitudinal push rod 4.

[0045] One end of each transverse push rod 5 is fixedly connected to the middle of one of the longitudinal push rods 4, and the other end of each transverse push rod 5 passes through the opening slot 7b and is fixedly connected to the inner ring of the central bearing 6a. The roller body 6 can rotate flexibly around the axis of the transverse push rod 5 through the central bearing 6a to realize steering adaptation in the power transmission process.

[0046] The wave height H between the crest and trough of the axial centerline of the wave-shaped double V-groove 7a of the rotating cylinder 7 is equal to the stroke of each piston 2, ensuring that the stroke of the piston reciprocating motion can be fully transmitted to the rotating cylinder 7, thereby achieving stable output of rotational motion.

[0047] The number of crests and troughs of the wave-shaped double V-groove 7a of the rotating cylinder 7 are equal, and the number of crests is equal to the number of cylinders, or the number of crests is an integer multiple of the number of cylinders, or the number of crests is half the number of cylinders, so as to adapt to different power output speed requirements.

[0048] The rotating column 7 has a first power shaft 8 and a second power shaft 9 at its two ends, respectively. One end of the first power shaft 8 is fixedly connected to one end of the rotating column 7, and the other end of the first power shaft 8 is fixedly connected to one end of the flywheel 13. The other end of the flywheel 13 is the first power output end 13a. One end of the second power shaft 9 is fixedly connected to the other end of the rotating column 7, and the other end of the second power shaft 9 is the second power output end 9a. The rotating column 7 is fixedly supported on the machine body 10 by two rolling bearings 11, which are respectively installed at both ends of the rotating column 7 near the power shafts to ensure stable rotation of the rotating column.

[0049] By selecting the appropriate cylinder 3 components, either compression ignition or spark ignition can be achieved for fuel combustion. The configuration of the cylinder 3 assembly using the ignition method is as follows: Each cylinder 3 has an electronic intake valve 1b, an electronic exhaust valve 1a, a spark plug 1c, and a combustion chamber on its corresponding cylinder head 1. The combustion chamber is formed by the inner surface of the cylinder head 1 and the top of the piston 2, and is not an independent component of the cylinder head. This solution primarily addresses the problems of insufficient ignition timing control precision and poor intake and exhaust coordination in traditional spark-ignition engines, leading to incomplete combustion, large power output fluctuations, and difficulty in adapting to the reciprocating rotary power transmission structure of this invention. The electronic intake and exhaust valves can achieve precise opening and closing timing control. Combined with the precise ignition of the spark plug, they can dynamically optimize the valve timing and ignition advance angle according to engine speed and load, improving fuel combustion efficiency and reducing exhaust emissions. It is more compatible with the opposed cylinders and reciprocating rotary power structure of this device, achieving smoother power output and avoiding power loss caused by valve timing lag in traditional engines. It is suitable for light-duty power scenarios with high requirements for power response speed and emissions.

[0050] The configuration of the cylinder 3 assembly using compression ignition is as follows: Each cylinder 3 has an electronic intake valve 1b, an electronic exhaust valve 1a, a high-pressure fuel injector 1d, and a combustion chamber on its corresponding cylinder head 1. The combustion chamber is formed by the inner surface of the cylinder head 1 and the top of the piston 2. This design optimizes traditional compression-ignition engines by addressing issues such as poor fuel atomization, poor coordination between air-fuel injection and valve timing, carbon buildup, excessive fuel consumption, and difficulty in adapting power output to reciprocating rotary transmission structures. The high-pressure fuel injector atomizes fuel into fine droplets, improving the uniformity of fuel-air mixing. Combined with precise valve timing via electronic valves, this achieves efficient compression ignition, reducing fuel consumption and carbon buildup. The opposed cylinder layout adapted to this device balances cylinder pressure during engine operation, reduces vibration, and improves the stability and continuity of power output. It is suitable for heavy-duty power applications requiring high torque and fuel economy, such as construction machinery and heavy vehicles.

[0051] Powertrains based on reciprocating rotary opposed linear piston engines include the following types: Powertrain 1: The first power output end 13a of the flywheel 13 is connected to the power input end of the high-voltage generator 16; the first power shaft 8 is provided with an independent power output end 8a, which is connected to the power input end of the low-voltage generator 15, forming a powertrain adapted to the application of range extenders for new energy vehicles.

[0052] This solution addresses the problems of existing new energy vehicle range extenders, which mostly employ a single power output structure, making it difficult to simultaneously meet the high-voltage power supply needs of the drive motor and the low-voltage power supply needs of onboard electrical appliances. Furthermore, these extenders often suffer from slow power response, low range replenishment efficiency, and poor compatibility with the vehicle's powertrain. By connecting dual power output terminals to high- and low-voltage generators respectively, independent and stable output of high and low voltage electricity can be achieved, balancing the high-voltage power supply needs of the onboard drive motor and the low-voltage power supply needs of various electrical appliances, thus avoiding the power supply bottleneck of a single generator structure.

[0053] The number of crests of the wave-shaped double V-groove 7a of the rotating cylinder 7 is half the number of cylinders. That is, the number of crests of the wave-shaped double V-groove 7a used by the four cylinders is two. Each cylinder works in a four-stroke ignition mode. The four cylinders complete one working cycle in sequence. The corresponding rotating cylinder 7, first power shaft 8, and second power shaft 9 rotate 360°. The speed output by the first power output end 13a of the flywheel 13 and the power output end 8a on the first power shaft 8 is twice as fast as the output speed of the traditional crank-connecting rod mechanism, so as to adapt to the high-speed, high-power generator.

[0054] The reciprocating rotary power transmission structure of this device has low power loss and fast response speed. It can dynamically adjust the power generation according to the vehicle's driving conditions, improve range extension efficiency, extend the driving range of new energy vehicles, and adapt to the power layout of new energy vehicles. The structure is compact, reduces the space occupied by the vehicle body, and improves the overall power performance and energy economy of the vehicle.

[0055] Powertrain 2: The first power output end 13a of the flywheel 13 is connected to the power input end of the automatic transmission 17; the power output end 8a of the first power shaft 8 is connected to the power input end of the low-voltage generator 15, forming a powertrain adapted to conventional automotive applications.

[0056] When the number of crests of the wave-shaped double V-groove 7a of the rotating cylinder 7 is the same as the number of cylinders, that is, the number of crests of the wave-shaped double V-groove 7a used in the four cylinders is four, each cylinder works in a four-stroke ignition mode, and the four cylinders complete one working cycle in sequence. The corresponding rotating cylinder 7, the first power shaft 8, and the second power shaft 9 rotate 180°. Then the speed output of the first power output end 13a of the flywheel 13 and the power output end 8a on the first power shaft 8 is one-quarter of the output speed of the traditional crank-connecting rod mechanism, which is equivalent to obtaining a reduction ratio of 4.0 to adapt to automobile engines and automatic transmissions. The flywheel 13, when connected to the automatic transmission, enables smooth power transmission, reduces power interruptions during gear shifts, and improves vehicle ride smoothness. The first power shaft 8, independently connected to a low-voltage generator, can simultaneously power onboard electrical systems while the vehicle is in motion, eliminating the need for an additional generator and simplifying the vehicle's powertrain structure. The opposed cylinders and reciprocating rotary structure of this device balance engine vibration, reduce noise during vehicle operation, improve power output efficiency, reduce power transmission losses, adapt to the powertrain layout of traditional automobiles, balance power performance and fuel economy, and reduce vehicle manufacturing and maintenance costs.

[0057] Powertrain 3: The first power output end 13a of the flywheel 13 is connected to the power input end of the hydraulic torque converter 18; the power output end 8a of the first power shaft 8 is connected to the power input end of the low-voltage generator 15, forming a powertrain adapted to engineering machinery applications.

[0058] When the number of crests of the wave-shaped double V-groove 7a of the rotating cylinder 7 is twice the number of cylinders, that is, when the number of crests of the wave-shaped double V-groove 7a used in the four cylinders is eight, each cylinder works in a four-stroke compression ignition mode. The four cylinders complete one working cycle in sequence. The corresponding rotating cylinder 7, the first power shaft 8, and the second power shaft 9 rotate 90°. Then, the speed output of the first power output end 13a of the flywheel 13 and the power output end 8a on the first power shaft 8 is one-eighth of the output speed of the traditional crank-connecting rod mechanism, which is equivalent to obtaining a reduction ratio of 8.0 to adapt to the power transmission of engineering machinery and meet the power output requirements of low speed and high torque.

[0059] This solution addresses the challenges of complex operating conditions and large load fluctuations in construction machinery, the unstable power output of traditional engines leading to overload damage, and the inability to meet the power supply needs of the equipment, resulting in poor adaptability. The hydraulic torque converter buffers load impacts, enabling flexible power transmission and preventing engine overload during heavy-load starts and frequent reversals, thus extending the service life of both the engine and the equipment. The dual-power output structure simultaneously meets the operational power requirements of the construction machinery and the low-voltage power supply needs of onboard and auxiliary equipment, eliminating the need for a separate generator and simplifying the equipment structure. The reciprocating rotary power transmission structure provides high torque and stable operation, adapting to the high and low load switching conditions of construction machinery, improving operational efficiency, reducing vibration and noise during operation, and making it suitable for complex outdoor working environments, thus lowering the equipment failure rate.

[0060] In this embodiment, the basic working principle by which the rotating cylinder 7, roller 6, longitudinal push rod 4, and transverse push rod 5 convert the reciprocating motion of the piston 2 into continuous unidirectional rotational motion and output power is as follows: (1) Each cylinder 3 of the engine operates in a four-stroke manner and in the firing order of cylinders I, II, III, and IV. That is, cylinder I is ignited during the power stroke, accompanied by the compression stroke of cylinder II, the intake stroke of cylinder III, and the exhaust stroke of cylinder IV. When cylinder I completes its power stroke and enters its exhaust stroke, cylinder II is ignited during its power stroke, accompanied by the compression stroke of cylinder III and the intake stroke of cylinder IV, and so on.

[0061] (2) When the engine starts, the starter 14 meshes with the gear ring of the flywheel 13. The starter 14 is energized and drives the flywheel 13, the first power shaft 8, and the rotating cylinder 7 to rotate synchronously. The wave-shaped double V-shaped groove 7a of the rotating cylinder 7 contacts the double cone surface 6b of the roller body 6. The groove contour pushes the roller body 6 to roll along the groove, while driving the transverse push rod 5 to move up and down. The transverse push rod 5 drives the longitudinal push rod 4 to reciprocate up and down along the cylinder axis, thereby pushing the piston 2 to reciprocate linearly within the cylinder 3. Each cylinder piston 2 sequentially completes the intake stroke from top dead center to bottom dead center, and then completes the compression stroke from bottom dead center to top dead center. Before reaching the top dead center of the compression stroke, spark plug 1c ignites the combustible mixture in the combustion chamber, generating high temperature and pressure, which pushes piston 2 from top dead center to bottom dead center to complete the power stroke. Piston 2 then completes the exhaust stroke from bottom dead center to top dead center. Then piston 2 completes the intake stroke from top dead center to bottom dead center, and the compression stroke from bottom dead center to top dead center, and so on, until the engine starts and the starter motor 14 is de-energized.

[0062] (3) When the engine is running normally, during the power stroke of each cylinder 3, the thrust generated by the piston 2 is transmitted to the roller body 6 through the longitudinal push rod 4 and the transverse push rod 5, pushing the roller body 6 to move downward or upward: when cylinder I or III is working, the roller body 6 is pushed downward, and the double cone surface 6b of the roller body 6 is in close contact with the lower V-shaped groove of the wavy double V-shaped groove 7a of the rotating cylinder 7; when cylinder I or IV is working, the double cone surface 6b of the roller body 6 is in close contact with the upper V-shaped groove of the wavy double V-shaped groove 7a of the rotating cylinder 7. Under the action of the circumferential shear force of the contact pressure between the double cone surface 6b of the roller body 6 and the wavy double V-shaped groove 7a of the rotating cylinder 7, the rotating cylinder 7 is pushed to rotate clockwise.

[0063] During the intake stroke of cylinder 3 in either cylinder I or III, the rotational inertia of flywheel 13 causes the wave-shaped double V-groove 7a of the rotating cylinder 7, coaxially connected to flywheel 13, to push the double-conical frustum 6b of roller 6, generating a downward force. This force drives the longitudinal push rod 4 and the transverse push rod 5, moving the piston 2 of cylinder 3 from top dead center to bottom dead center, thus completing the intake stroke. Similarly, the intake stroke of cylinder 3 in either cylinder II or IV is also achieved using the rotational inertia of flywheel 13.

[0064] During the exhaust or compression stroke of cylinder 3 (either cylinder I or cylinder III), the rotational inertia of flywheel 13 causes the wavy double V-shaped groove 7a of the rotating cylinder 7, coaxially connected to flywheel 13, to push the double conical frustum 6b of roller 6, generating a downward force. This force drives the longitudinal push rod 4 and the transverse push rod 5, moving the piston 2 of each cylinder from bottom dead center to top dead center, thus completing the exhaust or compression stroke. Similarly, the exhaust or compression stroke of cylinder 3 (either cylinder II or cylinder IV) is achieved using the rotational inertia of flywheel 13.

[0065] Because the wave-shaped double V-shaped grooves 7a are connected end to end, and with the continuous reciprocating motion of the pistons 2 of each cylinder, the rotating cylinder 7 rotates continuously in the predetermined direction under the coordinated push of each roller body 6, realizing continuous engine operation and transmission. Due to the use of multiple cylinders, the continuous operation and transmission of the engine are smoother, and stable power is output to the outside through the first power shaft 8, the second power shaft 9 and the flywheel 13.

[0066] (4) During engine start-up and normal operation, the electronic control unit collects the engine speed signal and piston top dead center position signal of each cylinder piston by the speed sensor 12 installed on the first drive shaft 8 or the flywheel 13, and accurately controls the opening and closing timing of the electronic intake valve 1b and electronic exhaust valve 1a of each cylinder, as well as the ignition timing of the spark plug 1c of each cylinder of the spark-ignition engine or the injection timing and injection quantity of the high-pressure injector 1d of each cylinder of the compression-ignition engine, to ensure stable and efficient engine operation.

[0067] The embodiments of this application have been described in detail above with reference to the accompanying drawings. However, this application is not limited to the above embodiments. Within the scope of knowledge possessed by those skilled in the art, various changes can be made without departing from the spirit of this application.

Claims

1. A reciprocating rotary opposed linear piston engine power unit, comprising a body (10), two or more pairs of opposing cylinders (3), wherein each pair of opposing cylinders (3) is symmetrically arranged circumferentially and axially along the body (10), each cylinder (3) is provided with a piston (2), and each cylinder (3) is provided with a cylinder head (1) at its top, characterized in that: It also includes a rotating cylinder (7), multiple rollers (6), multiple longitudinal push rods (4) and multiple transverse push rods (5); The rotating cylinder (7) is located at the center of the machine body (10) in both the axial and circumferential directions, and is fixedly supported on the machine body (10) by bearings (11). The axis of the rotating cylinder (7) is parallel to the axis of each pair of opposing cylinders (3). The middle section of the rotating cylinder (7) is provided with a wavy double V-shaped groove (7a) along the circumference of the cylinder. The two V-shaped grooves of the wavy double V-shaped groove (7a) are located at the two ends of the axial direction, and the wavy double V-shaped groove (7a) is connected end to end. The middle of the wavy double V-shaped groove (7a) is provided with an opening groove (7b) facing the cylindrical surface. The wavy double V-shaped groove (7a) is provided with a number of roller bodies (6), and each roller body (6) is provided with a central bearing (6a) at its center. The outer circumferential surface of the roller body (6) is a double cone frustum (6b) that is large in the middle and small at both ends. The included angle of the generatrix of the double-conical frustum (6b) of the roller body (6) is equal to the V-groove angle of the wavy double V-groove (7a), and the double-conical frustum (6b) of the roller body (6) and the double V-groove surface of the wavy double V-groove (7a) are arranged with a gap, and the roller body (6) rolls along the wavy double V-groove (7a); The longitudinal centerline of each longitudinal push rod (4) is parallel to the axial centerline of the rotating cylinder (7); each end of each longitudinal push rod (4) is connected to a piston (3); One end of each transverse push rod (5) is fixedly connected to the middle part (4) of one of the longitudinal push rods, and the axis of the transverse push rod (5) is perpendicular to the axis of the longitudinal push rod (4); the other end of each transverse push rod (4) passes through the opening slot (7b) and is fixedly connected to the center bearing hole of the center bearing (6a), and the roller body (6) rotates around the axis of the transverse push rod (5). The two ends of the rotating cylinder (7) are coaxially connected to a first power shaft (8) and a second power shaft (9). The end of the first power shaft (8) away from the rotating cylinder (7) is fixedly connected to one end of the flywheel (13). The other end of the flywheel (13) is the first power output end (13a). The end of the second power shaft (9) away from the rotating cylinder (7) is the second power output end (9a).

2. The reciprocating rotary opposed linear piston engine power unit according to claim 1, characterized in that: The distance from the longitudinal centerline of each longitudinal push rod (4) to the axial centerline of the rotating cylinder (7) is equal.

3. The reciprocating rotary opposed linear piston engine power unit according to claim 1, characterized in that: The wave height between the crest and trough of the wavy double V-shaped groove (7a) of the rotating cylinder (7) is equal to the stroke of each piston (2).

4. The reciprocating rotary opposed linear piston engine power unit according to claim 1, characterized in that: The number of crests and troughs of the wave-shaped double V-groove (7a) of the rotating cylinder (7) are equal, and the number of crests is equal to the number of cylinders (3), or the number of crests is an integer multiple of the number of cylinders (3), or the number of crests is half the number of cylinders.

5. The reciprocating rotary opposed linear piston engine power unit according to claim 1, characterized in that: The cylinder head (1) is equipped with an electronic intake valve (1b), an electronic exhaust valve (1a), a spark plug (1c), and a combustion chamber.

6. The reciprocating rotary opposed linear piston engine power unit according to claim 1, characterized in that: The cylinder head (1) is equipped with an electronic intake valve (1b), an electronic exhaust valve (1a), a high-pressure fuel injector (1d), and a combustion chamber.

7. A powertrain based on the reciprocating rotary opposed linear piston engine power unit as described in claim 1, characterized in that: The first power output end (13a) of the flywheel (13) is connected to the power input end of the high-voltage generator (16), and the second power output end (9a) of the second power shaft (9) is connected to the power input end of the low-voltage generator (15), forming a powertrain adapted to the application of range extenders for new energy vehicles.

8. A powertrain based on the reciprocating rotary opposed linear piston engine power unit as described in claim 1, characterized in that: The first power output end (13a) of the flywheel (13) is connected to the power input end of the automatic transmission (17), and the second power output end (9a) of the second power shaft (9) is connected to the power input end of the low-voltage generator (15), forming a powertrain adapted to conventional automobile applications.

9. A powertrain based on the reciprocating rotary opposed linear piston engine power unit as described in claim 1, characterized in that: The first power output end (13a) of the flywheel (13) is connected to the power input end of the hydraulic torque converter (18), and the second power output end (9a) of the second power shaft (9) is connected to the power input end of the low-voltage generator (15), forming a powertrain adapted to engineering machinery applications.

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