Connecting rod transmission mechanism and mirror image engine

Abstract

The invention relates to the technical field of mechanical transmission, and provides a connecting rod transmission mechanism and a mirror image engine. The connecting rod transmission mechanism comprises a power sliding block, a power connecting rod and two power pistons, the power connecting rod comprises a connecting rod base body and two linear rod parts, the linear rod parts extend in the first direction, the front end of each linear rod part is connected with one power piston, and the rear end of each linear rod part is fixedly connected with the connecting rod base body; the two linear rod parts are located on the two opposite sides of the connecting rod base body in the first direction, and the power sliding block is installed on the connecting rod base body in a sliding mode in the second direction. The linear rod part does not need to contain a bearing, rotation motion does not exist, the overall cross section is uniform or roughly uniform, standard sinusoidal motion / cosine motion is met, the size reduction design of the linear rod part and the air cylinder is facilitated, the compression ratio in the air cylinder is increased, the combustion efficiency is improved, the overall structure of the engine is more compact, and the needed engine cabin space is reduced. And the power-to-weight ratio and the acceleration performance of the vehicle can be improved.

Description

Technical Field

[0001] The invention relates to the technical field of mechanical transmission, in particular to a connecting rod transmission mechanism and a mirror engine. Background Art

[0002] The conventional engine uses a crank-connecting rod mechanism to connect the piston and the crankshaft. One end of the connecting rod is rotatably connected to the crank through a bearing, and the other end of the connecting rod is rotatably connected to the piston. Under the push of the piston, the connecting rod rotates, driving the crank and the crankshaft to rotate. Among them, please refer to Chinese patent announcement number CN221462733U. The connecting rod includes a small connecting rod head, a connecting rod body and a big connecting rod head connected in sequence. The big connecting rod head and the connecting rod cover enclose a bearing mounting hole for connecting with the crank, that is, the width of the big connecting rod head is at least greater than the outer diameter of the bearing, which increases the size of the big connecting rod head. In addition, the big connecting rod head is connected to the connecting rod cover through a connecting rod bolt, and a bolt mounting hole needs to be added in width, which further increases the size of the big connecting rod head, resulting in an increase in the size of the transition zone between the connecting rod body and the big connecting rod head.

[0003] In the crank-connecting rod mechanism of a traditional engine, the connecting rod has both reciprocating linear motion with the piston and rotational motion with the crank, which requires a larger space for movement. In addition, the connecting rod big end is large in size, and the transition zone between the connecting rod body and the connecting rod big end is large in size. Therefore, a larger cylinder bore (diameter) is needed to ensure that there is sufficient radial space inside the cylinder to prevent the connecting rod from interfering (colliding) with the inner wall of the cylinder when moving.

[0004] However, under the premise of unchanged engine displacement, large-bore, short-stroke engines are not conducive to improving fuel economy and compression ratio. The compression ratio is closely related to engine performance. Reasonable increase in compression ratio can effectively improve specific fuel consumption. Usually, low compression ratio refers to a compression ratio below 10, and high compression ratio refers to a compression ratio above 10. Summary of the invention

[0005] The purpose of the present invention is to provide a connecting rod transmission mechanism and a mirror image engine, aiming to solve the technical problem that the compression ratio of the existing engine needs to be improved.

[0006] In the first aspect, the present application provides a connecting rod transmission mechanism, which includes a power slider, a power connecting rod and two power pistons, the power connecting rod includes a connecting rod base and two straight rod portions, the straight rod portions extend along a first direction, the front end portion of each of the straight rod portions is connected to one of the power pistons, the rear end portion of the straight rod portion is fixedly connected to the connecting rod base, the two straight rod portions are located on opposite sides of the connecting rod base in the first direction, the power slider is slidably mounted on the connecting rod base in a second direction, and the first direction is perpendicular to the second direction.

[0007] In a second aspect, the present application provides a mirror image engine, the mirror image engine comprising a crankshaft, a torque elimination device, two cylinders and a connecting rod transmission mechanism as described in any one of the above, wherein the length direction of the crankshaft is consistent with a third direction, the crankshaft rotates around the third direction, and the crankshaft comprises at least one crank throw; the first direction, the second direction and the third direction are perpendicular to each other;

[0008] The power slider is rotatably mounted on the crank, and each power piston is slidably disposed in one of the cylinders along the first direction;

[0009] The torque elimination device includes a torque elimination mass block, which reciprocates along the first direction under the drive of the crankshaft. The inertia torque generated by the torque elimination mass block acting on the engine body is opposite to the inertia torque generated by all the connecting rod transmission mechanisms acting on the engine body.

[0010] The connecting rod transmission mechanism and the mirror image engine provided by the present invention have the following beneficial effects: the rear end of the linear rod is fixedly connected to the connecting rod base, and no bearing is required between the two, that is, the size of the rear end and the cylinder can be reduced in design; the front end of the linear rod is connected to the power piston, and the linear rod performs reciprocating linear motion in the cylinder along the first direction with the power piston, and there is no rotational motion, and the cylinder does not need to increase the cylinder diameter to leave a rotation space, and the cylinder and the linear rod do not interfere with each other, which is conducive to the reduction of the size of the cylinder; the shape of the linear rod is linear, and the overall cross-section is uniform or approximately uniform. Under the same structural strength requirements, the size of the linear rod with uniform cross-section can be reduced in design, the cylinder diameter accommodates the linear rod with uniform cross-section, and the internal space of the cylinder is fully utilized, which is conducive to improving the compression ratio of the cylinder; the power slider is assembled on the crankshaft and performs circular motion, and the power piston and the power connecting rod are the sub-motion of the circular motion in the first direction, and their displacement, velocity, acceleration and jerk are Both conform to the standard sine motion / cosine motion, so that the dynamic load borne by the linear rod is smaller than that of the traditional connecting rod, and there are fewer stress concentration points, which reduces the reliability problems caused by fatigue fracture and other failures, and is conducive to the size reduction design of the linear rod, and then to the further reduction of the cylinder diameter design. At the same time, the compact structure also helps to reduce vibration and noise, and improve the overall durability of the engine; based on this, under the premise that the engine displacement remains unchanged, reducing the cylinder diameter can increase the stroke of the power piston accordingly. A longer piston stroke means that in the compression stroke, on the one hand, the compression ratio in the cylinder can be increased, which helps to make more full use of the energy of the fuel and improve the combustion efficiency, thereby improving the thermal efficiency and power output of the engine; on the other hand, it can reduce the loss of unburned fuel, thereby reducing fuel consumption and improving fuel economy; on the third hand, a smaller cylinder diameter means that the contact area between the power piston and the cylinder wall is reduced, which helps to reduce the friction between the two. In this way, the cylinder bore and the size of the power connecting rod are reduced, which solves the technical problem that the existing engine compression ratio needs to be improved. It can make the overall structure of the engine more compact, reduce the required engine compartment space, and help improve the vehicle's power-to-weight ratio and acceleration performance. BRIEF DESCRIPTION OF THE DRAWINGS

[0011] In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative labor.

[0012] Figure 1 A schematic diagram of the assembly of a connecting rod transmission mechanism and a cylinder provided in an embodiment of the present invention;

[0013] Figure 2 for Figure 1 Section view along line AA;

[0014] Figure 3 Schematic diagram for comparing the displacement of a power piston and a conventional piston;

[0015] Figure 4 A schematic diagram showing the speed comparison between the power piston and the conventional piston;

[0016] Figure 5 It is a schematic diagram comparing the acceleration of the power piston and the traditional piston;

[0017] Figure 6 A schematic diagram comparing the jerkiness of a power piston and a conventional piston;

[0018] Figure 7 A schematic structural diagram of a power connecting rod of a connecting rod transmission mechanism provided by an embodiment of the present invention;

[0019] Figure 8 A schematic cross-sectional view of a power connecting rod of a connecting rod transmission mechanism;

[0020] Fig. 9 Schematic diagrams of eight cross sections of a power connecting rod of a connecting rod transmission mechanism;

[0021] Fig.10 An exploded view of a connecting rod transmission mechanism provided by an embodiment of the present invention;

[0022] Fig.11 It is a schematic diagram of the installation of the power piston of the connecting rod transmission mechanism;

[0023] Fig.12 It is a lubrication schematic diagram of the power slider of the connecting rod transmission mechanism;

[0024] Fig.13 A schematic diagram of the structure of the mirror engine provided in this embodiment;

[0025] Fig.14 A schematic diagram of another structure of the mirror engine provided in this embodiment;

[0026] Fig.15 for Figure 1 A first structural schematic diagram of a torque elimination device of a mirror image engine;

[0027] Fig.16 for Figure 1 A second structural schematic diagram of the torque elimination device of the mirror image engine;

[0028] Fig.17 for Figure 1 A third structural schematic diagram of the torque elimination device of the mirror image engine;

[0029] Fig.18 for Figure 1 A schematic diagram of the assembly of the second rotating wheel and the torque elimination pin of the torque elimination device;

[0030] Fig.19 for Fig.18 Right sectional view of .

[0031] Among them, the reference numerals in the figure are:

[0032] X, first direction; Y, second direction; Z, third direction;

[0033] 10. Crankshaft; 11. Crank; 12. Axis; 13. Rotation trajectory; 14. Cylinder;

[0034] 20. Connecting rod transmission mechanism; 21. Lubricating layer; 22. Power slider; 221. Third flow channel; 23. Power connecting rod; 231. Connecting rod base; 232. Linear rod; 233. Front end; 234. Rear end; 235. First sliding groove; 236. Linear guide; 24. Power piston; 241. Clamping groove; 25. Piston pin; 26. Power bearing; 261. Oil hole; 262. First flow channel; 263. Second flow channel; 264. First sub-flow channel; 265. Second sub-flow channel; 27. Clamping ring;

[0035] 30. Torque elimination device; 31. Torque elimination mass block; 311. Second sliding groove; 32. First rotating wheel; 33. Second rotating wheel; 34. Torque elimination slider; 341. Slider track; 35. Torque elimination pin; 36. Torque elimination bearing; 371. Synchronous belt; 372. Transmission gear; 38. Torque elimination guide rail; 39. Rolling body. DETAILED DESCRIPTION

[0036] Embodiments of the present invention are described in detail below, examples of which are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are intended to be used to explain the present invention, and should not be construed as limiting the present invention.

[0037] Reference throughout the specification to "one embodiment" or "an embodiment" means that a particular feature, structure, or characteristic described in connection with the embodiment is included in at least one embodiment of the present application. Thus, when the phrases "in one embodiment" or "in some embodiments" appear in various places throughout the specification, not all references are to the same embodiment. Furthermore, in one or more embodiments, the particular features, structures, or characteristics may be combined in any suitable manner.

[0038] In the description of the present invention, it should be understood that the terms "length", "width", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", etc., indicating the orientation or position relationship are based on the orientation or position relationship shown in the drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present invention.

[0039] In addition, the terms "first" and "second" are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Thus, the features defined as "first" and "second" may explicitly or implicitly include one or more of the features.

[0040] In the present invention, unless otherwise clearly specified and limited, the terms "installed", "connected", "connected", "fixed" and the like should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, it can be the internal connection of two elements or the interaction relationship between two elements. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0041] Embodiment 1

[0042] Combination Figure 1 and Figure 2 The connecting rod transmission mechanism 20 provided in the present application includes a power slider 22, a power connecting rod 23 and two power pistons 24. The power connecting rod 23 includes a connecting rod base 231 and two linear rods 232, the linear rods 232 extend along a first direction X, the front end 233 of each linear rod 232 is connected to a power piston 24, the rear end 234 of the linear rod 232 is fixedly connected to the connecting rod base 231, the two linear rods 232 are located on opposite sides of the connecting rod base 231 in the first direction X, and the power slider 22 is slidably mounted on the connecting rod base 231 along a second direction Y, and the first direction X and the second direction Y are perpendicular.

[0043] In this embodiment, the rear end portion 234 of the linear rod portion 232 is fixedly connected to the connecting rod base 231, and no bearing is required between the two, that is, the size of the rear end portion 234 can be reduced in design, and the cylinder diameter of the cylinder 14 can be reduced in design accordingly. The front end portion 233 of the linear rod portion 232 is connected to the power piston 24, and the linear rod portion 232 moves back and forth in the cylinder 14 along the first direction X with the power piston 24. The linear rod portion 232 does not rotate. The cylinder 14 does not need to increase the cylinder diameter to leave space for the linear rod portion 232 to rotate. The cylinder 14 does not interfere with the linear rod portion 232, which is conducive to further reducing the size of the cylinder 14.

[0044] In this embodiment, the shape of the straight rod 232 is straight, and the overall cross section is uniform or approximately uniform. Under the same structural strength requirements, the size of the straight rod 232 with a uniform cross section can be reduced in design, and the cylinder diameter of the cylinder 14 accommodates the straight rod 232 with a uniform cross section. The internal space of the cylinder 14 is fully utilized, and the compact fit helps to reduce vibration and noise, and improve the overall durability of the engine; the cylinder 14 with the same cylinder diameter can allow the straight rod 232 to have a larger stroke in the first direction X, and the power arm of the power connecting rod 23 to the crankshaft 10 is larger during the power stroke, and the torque generated on the crankshaft 10 is larger, which is beneficial to improving the power of the engine. In addition, the increased stroke of the straight rod 232 is beneficial to improving the compression ratio and thermal efficiency of the mirror engine. In the power stage, the energy generated by the combustion of the mixed gas inside the cylinder 14 can be efficiently converted into mechanical energy, which is beneficial to improving the power and economy of the mirror engine and achieving the effect of energy saving and emission reduction.

[0045] In this embodiment, combined with Figure 1 , Figure 2 and Fig.13 , the power slider 22 is installed on the crankshaft 10, and the power slider 22 moves in a plane along the rotation trajectory 13 with the crank 11. The power connecting rod 23 is responsible for transmitting the gas pressure on the power piston 24 generated by the combustion of the fuel in the cylinder 14 to the crankshaft 10, and outputting power to the outside. Taking the connecting rod transmission mechanism 20 close to the positive direction of the third direction Z as an example, the plane motion of the power slider 22 can be decomposed into linear motion in the first direction X and the second direction Y respectively. The displacement of the power slider 22 is x=r*(1-cosφ), y=r*sinφ, which is a standard sine motion / cosine motion, where r is the distance from the power slider 22 to the axis 12 of the crankshaft 10, which is a constant; φ is the angle between the line from the center of the power slider 22 to the axis 12 and the horizontal plane, or the angle of rotation of the power slider 22 relative to the xoz plane, which is a variable with a value range of 0 to 2π. The power piston 24 and the power connecting rod 23 make linear reciprocating motion along the first direction X (see Figure 3), the position of the power slider 22 in the first direction X, that is, x = r*(1-cosφ), the displacement expression is derived once, twice and three times, and the speed of the power piston 24 and the power connecting rod 23 can be obtained (see Figure 4 ), acceleration (see Figure 5 ) and jerk (see Figure 6 ), are monomial sine / cosine functions, the influencing factors are single, the mechanism is simple and reliable, there are no polynomial functions of sine / cosine, no second-order reciprocating inertia force is generated, and the power output is stable. In other words, the components of the connecting rod transmission mechanism 20 that move linearly only generate first-order reciprocating inertia force, and no second-order reciprocating inertia force is generated.

[0046] The conventional piston is connected to the crankshaft 10 through a connecting rod and a crank. The displacement expression of the piston in the first direction X is x=R*[(1-cosθ)+(1-cos2θ)*λ / 4]. Among them, R is the length of the crank, which is a constant; L is the length of the connecting rod, which is a constant; λ=R / L, which is a constant; θ is the angle between the crank and the horizontal plane, or the rotation angle of the crank relative to the xoz plane, which is a variable with a value range of 0 to 2π. Similarly, the velocity, acceleration and jerk of the conventional piston can be obtained by taking the first, second and third derivatives of the expression respectively. The high-speed reciprocating swing of the traditional connecting rod around the traditional piston inevitably generates lateral pressure on the traditional piston, causing the traditional piston group to make lateral translation and rotational swinging motions in the cylinder 14, which not only complicates the design and manufacture of the internal combustion engine, but also causes vibration of the internal combustion engine, which is one of the main vibration and noise sources of the engine; secondly, it causes friction and wear between the traditional piston and the wall of the cylinder 14, resulting in a large amount of energy loss, affecting the economy and power of the engine, and seriously endangering the service life and reliability of the engine; thirdly, the small end of the connecting rod makes reciprocating linear motion around the traditional piston, and the big end of the connecting rod rotates around the crankshaft 10, and the connecting rod as a whole performs a variable speed compound motion, so the multi-order inertial force generated during the movement of the connecting rod cannot be effectively balanced, which is another source of engine vibration and noise; fourthly, the engine gas pressure cannot form torque with the optimized lever arm.

[0047] Figures 3 to 6 Schematic diagram comparing the power piston 24 and the conventional piston in terms of displacement, velocity, acceleration and jerkiness, wherein curve A represents the power piston 24 and curve B represents the conventional piston.

[0048] Further analysis combined with Figure 3 The power connecting rod 23 provided in the present application performs pure cosine / sine motion, which is convenient for achieving complete dynamic balance. The traditional piston performs approximate cosine / sine motion, which is difficult to achieve complete dynamic balance; the envelope area of ​​the motion curve of the power piston 24 is smaller, the moving parts consume less energy, and more chemical energy is used to output torque.

[0049] Combination Figure 4 When the rotation angle of the horizontal axis is 180° or a single multiple of π, the power piston 24 leaves the top dead center position more slowly, that is, the engine will have a lower cylinder 14 volume change rate near the top dead center, maintain a gas state with a higher filling density, help the expansion of the combustion flame front, facilitate full combustion, facilitate environmental emissions, and facilitate the full conversion of chemical energy into mechanical energy; when the rotation angle of the horizontal axis is 180° or a multiple of 2π, the power piston 24 approaches the bottom dead center position more slowly, which helps prevent knocking and facilitates the use of low-grade fuel under the premise of a high compression ratio. Compared with a conventional crank-connecting rod mechanism engine with the same cylinder diameter and stroke, the movement of the power piston 24 after the top dead center has a lower speed, and the volume difference of the cylinder 14 reaches a peak between 10% and 20% between the top dead center and the bottom dead center.

[0050] Combination Figure 5 , the acceleration curve of the power piston 24 is smoother, the fluctuation is smaller, and the output torque is more stable. Figure 6 When the power slider 22 is in the middle position of the connecting rod base 231, it is on the x-axis with the power piston 24, the lever arm is 0, the mixed gas is ignited, the gas pressure in the cylinder 14 increases rapidly, the jerk of the power piston 24 is the largest, but at this time the lever arm of the power connecting rod 23 to the crankshaft 10 is the smallest. When the power slider 22 moves to the upper / lower dead center, the power piston 24 moves half of the stroke. Although the lever arm is the largest at this time, the gas pressure has dropped by more than half. In this way, the power piston 24 has a smaller impact and is smoother, which is beneficial for the connecting rod transmission mechanism 20 and the mirror engine to obtain better NVH performance.

[0051] In addition, since the displacement, velocity, acceleration and jerk of the power piston 24 and the power connecting rod 23 all conform to the standard sine motion / cosine motion, the dynamic load borne by the linear rod 232 is smaller than that of the traditional connecting rod, and the stress concentration points are also fewer, which reduces the reliability problems caused by failures such as fatigue fracture, and is conducive to reducing the strength requirements of the linear rod 232, that is, the dimensions of the linear rod 232, the cylinder 14, the power piston 24, etc. can be reduced in design, the cylinder 14 can be thin-walled, and the power piston 24 and the power connecting rod 23 can be lightweight, so as to achieve the lightweight of the connecting rod transmission mechanism 20 and reduce the inertia force of reciprocating motion. At the same time, the transition area between the linear rod 232 and the connecting rod base 231 is subjected to less force, and there is no need to adopt a large arc transition design.

[0052] In summary, under the premise that the engine displacement remains unchanged, reducing the cylinder diameter of the cylinder 14 can increase the stroke of the power piston 24 accordingly. A longer piston stroke means that in the compression stroke, the power piston 24 reaches deeper into the cylinder 14. On the first hand, it can increase the compression ratio in the cylinder 14, which helps to make more effective use of the energy of the fuel, improve combustion efficiency, and thus improve the thermal efficiency and power output of the engine; on the second hand, it has sinusoidal motion characteristics, which can reduce the loss of unburned fuel, thereby reducing fuel consumption and improving fuel economy; on the third hand, the smaller cylinder diameter of the cylinder 14 means that the contact area between the power piston 24 and the cylinder wall of the cylinder 14 is reduced, which is beneficial to reduce the friction between the two.

[0053] In some embodiments, in combination Figure 2 and Figure 7 , the two linear rods 232 are symmetrically distributed about the center of the connecting rod base 231. Specifically, the two linear rods 232 are respectively connected to the middle position of the connecting rod base 231 in the second direction Y. The two linear rods are mirror-imaged with respect to the connecting rod base 231. In this way, the two power pistons 24 are coaxially mirror-imaged and symmetrically arranged, which fundamentally solves the problem of weak sliding surface strength of a single-piston connecting rod and horizontal torsional vibration of multiple pistons.

[0054] In some embodiments, in combination Figure 2 and Figure 7 The rear end portion 234 is connected to the connecting rod base 231 by a rounded transition. The rounded transition can effectively disperse and alleviate the stress concentration phenomenon generated at the connection point, thereby improving the fatigue strength and durability of the power connecting rod 23. There is no need to increase the size of the rear end portion 234 to cope with the larger concentrated stress, which is conducive to the size reduction design of the straight rod portion 232 and the cylinder 14.

[0055] In some embodiments, the engine equipped with the connecting rod transmission mechanism has a high compression ratio, which effectively improves specific fuel consumption.

[0056] In one embodiment, in combination Figure 2 and Figure 7 The fillet diameter between the rear end portion 234 and the connecting rod base 231 is 50% to 180% of the diameter of the straight rod portion 232. On the one hand, the fillet diameter is greater than or equal to 50% of the diameter of the straight rod portion 232, so as to avoid the formation of a sharp corner at the rear end portion 234 and excessive local stress at the connection, which helps to better disperse the stress at the connection and improve the fatigue strength and durability of the entire power connecting rod 23; on the other hand, the fillet diameter is less than or equal to 180% of the diameter of the straight rod portion 232, so as to avoid the fillet transition size being too large and interfering with the cylinder wall of the cylinder 14.

[0057] Optionally, the fillet diameter is 120% to 150% of the diameter of the straight rod portion 232. For example, the fillet diameter is 120%, 130%, 140% or 150% of the diameter of the straight rod portion 232.

[0058] In this embodiment, the first direction X, the second direction Y and the third direction Z are perpendicular to each other.

[0059] In some embodiments, a dimension of the linear rod portion 232 in the third direction Z is close to a dimension of the connecting rod base 231 in the third direction Z.

[0060] In one of the embodiments, the size of the straight rod portion 232 in the third direction Z is 80% to 120% of the size of the connecting rod base 231 in the third direction Z, ensuring that the size of the straight rod portion 232 in the third direction Z is similar to the size of the connecting rod base 231, enhancing the connection strength between the straight rod portion 232 and the connecting rod base 231, avoiding dimensional redundancy of a certain component at the connection point in the third direction Z, and improving the compactness of the power connecting rod 23 in three-dimensional space.

[0061] Optionally, in the third direction Z, the size of the straight rod portion 232 is 80%, 90%, 100%, 110% or 120% of the size of the connecting rod base 231 .

[0062] In one embodiment, the size of the straight rod portion 232 in the second direction Y is 8% to 20% of the size of the connecting rod base 231 in the second direction Y. Since the power slider 22 is slidably disposed on the connecting rod base 231 along the second direction Y, the size of the connecting rod base 231 in the second direction Y is relatively large. This solution is conducive to reducing the size of the straight rod portion 232 by limiting the size of the straight rod portion 232 in the second direction Y to be less than or equal to 20% of the size of the connecting rod base 231, which helps to reduce its inertial force during movement and reduce the cylinder diameter of the cylinder 14. At the same time, this solution limits the size of the straight rod portion 232 in the second direction Y to be greater than or equal to 8% of the size of the connecting rod base 231 through simulation and strength verification, thereby avoiding unstable structural transition at the connection between the two and thus avoiding stress concentration.

[0063] Optionally, in the second direction Y, the size of the straight rod portion 232 is 8%, 10%, 12%, 15%, 18% or 20% of the size of the connecting rod base 231 .

[0064] In one of the embodiments, the straight rod portion 232 and the connecting rod base 231 are integrally formed to improve the integrity of the power connecting rod 23, avoid connection gaps and connection stresses between the two, avoid assembly errors, and comprehensively improve the structural strength of the power connecting rod 23, and prevent the connecting rod base 231 and the straight rod portion 232 from being significantly deformed during operation. Due to the improvement in strength and rigidity, the straight rod portion 232 and the cylinder 14 can be further reduced in size.

[0065] In one of the embodiments, welding, threaded connection, and interference fit between the linear rod portion 232 and the connecting rod base 231 do not require the use of connecting rod bolts, and the rear end portion 234 does not need to be enlarged to provide a screw hole, which is conducive to the reduction of the linear rod portion 232 and the cylinder 14. In addition, welding, threaded connection, and interference fit can ensure a tight connection between the linear rod portion 232 and the connecting rod base 231, reducing the strength drop caused by loose connection or breakage.

[0066] In one embodiment, compared to the conventional connecting rod big end which needs to be installed with bearings and fasteners, the linear rod portion 232 and the connecting rod base 231 are connected by fasteners, and the size of the rear end portion 234 is still smaller than that of the conventional connecting rod big end, which is conducive to the reduction of the linear rod portion 232 and the cylinder 14. In addition, the fasteners can facilitate the assembly and disassembly of the linear rod portion 232 and the connecting rod base 231, which helps to reduce the assembly difficulty and maintenance cost.

[0067] In some embodiments, in combination Figure 2 and Figure 7 The connecting rod base 231 has a first sliding groove 235 extending along the second direction Y, and the power slider 22 is slidably disposed in the first sliding groove 235. The first sliding groove 235 provides a precise guide path for the power slider 22, ensuring that it can maintain a stable and non-deflected motion state during the sliding process.

[0068] In one embodiment, in combination Figure 2 and Figure 7 The groove wall of the first sliding groove 235 has a linear guide rail 236, and the power slider 22 is slidably arranged on the linear guide rail 236. The linear guide rail 236 enhances the supporting effect of the base on the power slider 22, and the cooperation between the linear guide rail 236 and the power slider 22 can reduce the vibration caused by friction and clearance, and improve the transmission efficiency.

[0069] Specifically, the linear guide rail 236 is integrally formed on the groove wall of the first sliding groove 235 .

[0070] Specifically, there are two linear guide rails 236 , and the two linear guide rails 236 are disposed on two groove walls of the first sliding groove 235 in the first direction X.

[0071] In some embodiments, in combination Figure 7 and Figure 8 The power connecting rod 23 is subjected to periodic alternating loads during operation and is prone to fatigue fracture. The cross-sectional shape of the connecting rod base 231 and / or the straight rod portion 232 perpendicular to the first direction X is a W-shaped shape. Compared with the I-shaped connecting rod, the strength and rigidity of the connecting rod base 231 and / or the straight rod portion 232 are improved, which can prevent the power connecting rod 23 from being significantly deformed when transmitting power.

[0072] The middle part of the connecting rod base 231 has a first sliding groove 235, and the connecting rod base 231 has rod parts on both sides of the first sliding groove 235 in the second direction Y. The cross-sectional shape of the connecting rod base 231 perpendicular to the first direction X refers to the cross-sectional shape of the rod part perpendicular to the first direction X.

[0073] It can be understood that in other embodiments, Figure 7 and Fig. 9 The cross-sectional shape of the connecting rod base 231 and / or the straight rod portion 232 perpendicular to the first direction X is an I-shaped, quadrilateral, circular, elliptical, circular ring or elliptical ring. Among them, the connecting rod base 231 and / or the straight rod portion 232 with an I-shaped cross section has better bending resistance when subjected to bending load; the connecting rod base 231 and / or the straight rod portion 232 with a quadrilateral cross section has a simple shape and is easy to manufacture and process; under the same cross section and the same torque conditions, the maximum shear stress of the connecting rod base 231 and / or the straight rod portion 232 on the circular cross section is the smallest, and the torsion angle is also smaller than that of the non-circular cross-sectional axis; the connecting rod base 231 and / or the straight rod portion 232 with an elliptical cross section can provide a strong and weak axis that is beneficial to the structure under unidirectional compression bending, which is conducive to fully utilizing the material strength and saving materials. The connecting rod base 231 and / or the straight rod portion 232 with circular ring and elliptical ring cross sections have reasonable support and force performance, can evenly distribute the load, and improve the stability of the overall structure.

[0074] In some embodiments, in combination Figure 7 , the dimension of the linear rod 232 in the first direction X is 4 to 7 times the outer diameter of the linear rod 232. On the one hand, by increasing the dimension of the linear rod 232 in the first direction X to be greater than or equal to 4 times the outer diameter of the linear rod 232, the stroke of the linear rod 232 and the power piston 24 is increased, and the compression ratio of the cylinder 14 is increased; on the other hand, the dimension of the linear rod 232 in the first direction X is limited to be less than or equal to 7 times the outer diameter of the linear rod 232, so as to avoid the linear rod 232 being too thin, so that the linear rod 232 has good bending resistance when subjected to bending load.

[0075] Optionally, a dimension of the straight rod portion 232 in the first direction X is 4 times, 5 times, 6 times or 7 times the outer diameter of the straight rod portion 232 .

[0076] In some embodiments, in combination Fig.10 The connecting rod transmission mechanism 20 also includes a power bearing 26, which is installed in the power slider 22, so that the power slider 22 can be rotatably installed on the crankshaft 10, reducing the friction between the power slider 22 and the crankshaft 10.

[0077] In one embodiment, in combination Fig.10 and Fig.12 , an oil hole 261 is provided in the middle of the dynamic bearing 26. The design of the oil hole 261 enables the lubricating oil to be accurately delivered to the dynamic bearing 26, thereby significantly reducing the friction and wear between the dynamic slider 22 and the dynamic bearing 26, and between the dynamic bearing 26 and the crankshaft 10. The inner ring of the dynamic bearing 26 surrounds the oil hole 261, and the crank 11 is fixedly penetrated in the oil hole 261. The lubricating oil enters the dynamic bearing 26 from the gap between the crank 11 and the inner ring of the dynamic bearing 26.

[0078] Specifically, combined Fig.12 A lubricating layer 21 is provided between the power slider 22 and the connecting rod base 231. In the ignition / power stroke, the thrust in the first direction X is large, and the lubricating layer 21 realizes dynamic pressure lubrication or elastohydrodynamic lubrication to reduce friction and wear, thereby improving the overall efficiency and service life of the engine.

[0079] Optionally, combined Fig.12 The dynamic bearing 26 has a first flow channel 262 distributed in the radial direction and a second flow channel 263 distributed in the circumferential direction of the surface. The first flow channel 262 distributed in the radial direction is connected to the oil hole 261. The first flow channel 262 rotates with the crankshaft 10 to be connected or disconnected with the second flow channel 263. The first flow channel 262 guides the lubricating fluid flowing out of the oil hole 261 to flow to the second flow channel 263 on the surface of the dynamic bearing 26, thereby achieving a dynamic pressure lubrication effect.

[0080] Specifically, the power slider 22 has a third flow channel 221, and the third flow channel 221 is connected to the second flow channel 263 and the lubricating layer 21 respectively. When the power bearing 26 rotates, the second flow channel 263 guides the flow of lubricating fluid, establishes a stable lubricating layer 21, provides sufficient lubricating oil, and realizes reliable lubrication, thereby avoiding possible oil film rupture of the lubricating layer 21 and causing direct contact of the rough peaks. The lubricating oil further flows to the lubricating layer 21 through the third flow channel 221, so that the lubricating fluid overflowing from the third flow channel 221 and flowing out of the surface of the power slider 22 quickly spreads on the surface of the friction pair, especially the distal area away from the oil hole 261, thereby reducing the friction and wear between the power slider 22 and the connecting rod base 231. Based on this, since the third flow channel 221 can supply sufficient lubricating oil, there is no need to open a large-sized oil groove on the surface of the power slider 22, thereby avoiding reducing the structural strength of the power slider 22 and increasing the surface roughness of the power slider 22.

[0081] The connecting rod base 231 performs linear reciprocating motion, and the friction pair between the power slider 22 and the connecting rod base 231 changes back and forth with the sliding direction, and the load changes dramatically. Based on the motion law of the connecting rod base 231, the power slider 22 and the connecting rod base 231 are only subjected to force on one side at the same time, that is, only one side of the power slider 22 and the inner surface of the connecting rod base 231 are in close contact with each other at the same time to form a friction pair.

[0082] Optionally, the second flow channels 263 are distributed in a interconnected crisscross pattern on the outer surface of the dynamic bearing 26 to expand the lubrication area.

[0083] Among them, the lubricating oil may be unevenly distributed in the second flow channel 263 and easily flow out. The power slider 22 reciprocates up and down, and the reversal and speed changes affect the stability of the lubricating layer 21. The power slider 22 has two friction surfaces. In one rotation cycle, the two friction surfaces alternately form a friction pair with the connecting rod base 231, that is, any friction surface on the power slider 22 is not constant as a friction pair. This alternating characteristic makes the lubricating layer 21 quickly rupture and fail due to the increase in the gap between the friction pairs when it is separated from the friction pair, and the gap is in an oil-poor state. When the friction pair is formed again, the friction lubrication will be greatly affected due to insufficient oil supply.

[0084] Optionally, combined Fig.12 , the outer ring of the dynamic bearing 26 is fixed to the dynamic slider 22, and the second flow channel 263 of the outer ring of the dynamic bearing 26 includes a first sub-flow channel 264 and a second sub-flow channel 265, and the first sub-flow channel 264 and the second sub-flow channel 265 are respectively located on opposite sides of the outer ring of the dynamic bearing 26 in the first direction X. The first sub-flow channel 264 is located in the positive direction of the first direction X compared with the second sub-flow channel 265. The second flow channel 263 is always connected with the third flow channel 221. The inner ring of the dynamic bearing 26 rotates synchronously with the crankshaft 10 relative to the outer ring. When the power connecting rod 23 slides in the positive direction of the first direction X, the first flow channel 262 is connected with the first sub-flow channel 264 and disconnected from the second sub-flow channel 265; when the power connecting rod 23 slides in the negative direction of the first direction X, the first flow channel 262 is connected with the second sub-flow channel 265 and disconnected from the first sub-flow channel 264. Based on this, in accordance with the sinusoidal motion law of the power connecting rod 23, the first flow channel 262 is alternately connected to the first sub-flow channel 264 and the second sub-flow channel 265, so that the lubricating oil is concentratedly supplied to the side of the power slider 22 and the power connecting rod 23 where friction is occurring, so as to realize the targeted supply of lubricating oil. The supply of lubricating oil is increased on the side where the friction pair occurs, effectively reducing friction and wear. While ensuring reliable lubrication, excessive pump oil loss and reduced efficiency are avoided.

[0085] In this embodiment, combined with Fig. 9, the straight rod 232 can be solid or hollow. When the straight rod 232 is hollow, the hollow structure is used to allow lubricating oil to circulate, realize the heat dissipation function, ensure that the straight rod 232 can maintain a suitable working temperature under high-frequency and high-load conditions, prevent performance degradation or damage caused by overheating, and help reduce the heat load of the straight rod 232 to prevent its failure. In addition, when the crankshaft 10 box blowby occurs, the hollow structure can reduce the airflow disturbance in the crankshaft 10 box caused by the movement of the power connecting rod 23, which is conducive to the normal operation of the ventilation system in the crankshaft 10 box.

[0086] Optionally, the power connecting rod 23 has an oil supply channel 237, and the oil supply channel 237 is connected to the lubricating layer 21. In other words, the connecting rod base 231 and the linear rod portion 232 both have the oil supply channel 237 and are connected to each other.

[0087] In some embodiments, in combination Fig.10 and Fig.11 The connecting rod transmission mechanism 20 also includes a piston pin 25 and two snap rings 27. The front end portion 233 has a through pin hole. The two ends of the power piston 24 have snap grooves 241 respectively. The two snap rings 27 are respectively snapped into the two snap grooves 241. The piston pin 25 is inserted into the pin hole. The two ends of the piston pin 25 are respectively against the two snap rings 27 to limit the position of the piston pin 25. Specifically, the power piston 24 is rotatably connected to the straight rod portion 232, connected by the piston pin 25 and movable along the axial direction of the piston pin 25, which releases the strong motion constraint between the power connecting rod 23 and the cylinder 14, so that the power connecting rod 23 is in an adaptive and self-balancing floating state, solves the problem that the two mirror-opposed cylinders 14 are not perpendicular to the axis 12 of the crankshaft 10 due to the thermal expansion of the cylinder 14 or the bending and torsion deformation of the crankshaft 10, reduces the processing and assembly precision requirements, and greatly prolongs the service life.

[0088] In one embodiment, the power slider 22 is rotatably mounted on the connecting rod journal of the crank 11 through the power bearing 26. The power slider 22 moves on the plane xoy as the crankshaft 10 rotates, which can be decomposed into a linear reciprocating motion along the first direction X and a linear reciprocating motion along the second direction Y in the first sliding groove 235. The rotation track 13 of the center of the power slider 22 is circular. The power slider 22 and the power connecting rod 23 transmit power through the sliding pair. The power connecting rod 23 does not have a reciprocating swing around the piston pin 25, thereby improving the efficiency of power transmission.

[0089] Embodiment 2

[0090] To simplify the drawing, Fig.13 and Fig.14 Only the straight rod portion 232 is illustrated, and it is not illustrated that the outer diameter of the straight rod portion 232 along the first direction X remains substantially unchanged.

[0091] Combination Fig.13 and Fig.14 The present application provides a mirror engine, which includes a crankshaft 10, a torque elimination device 30, two cylinders 14 and a connecting rod transmission mechanism 20 of any one of the first embodiments. The length direction of the crankshaft 10 is consistent with the third direction Z, the crankshaft 10 rotates around the third direction Z, and the crankshaft 10 includes at least one crank 11. In other words, the number of cranks 11 can be one, two, or more than two, which is not specifically limited here. The first direction X, the second direction Y and the third direction Z are perpendicular to each other. The power slider 22 is rotatably mounted on the crank 11, and one power slider 22 corresponds to one crank 11. That is, the number of cranks 11 is greater than or equal to the number of connecting rod transmission mechanisms 20, and each crank 11 can be equipped with a connecting rod transmission mechanism 20, or some cranks 11 can be equipped with connecting rod transmission mechanisms 20, and some cranks 11 are idle. Generally, the number of cranks 11 is equal to the number of connecting rod transmission mechanisms 20, and they correspond one to one. Each power piston 24 can be slidably arranged on a cylinder 14 along the first direction X.

[0092] The torque elimination device 30 includes a torque elimination mass block 31, which reciprocates along the first direction X under the drive of the crankshaft 10. The inertia torque generated by the torque elimination mass block 31 acting on the engine body is opposite to the inertia torque generated by all connecting rod transmission mechanisms 20 acting on the engine body.

[0093] Please continue to see Fig.13 For a four-cylinder horizontal mirror engine, since the phase angles of the two cranks 11 differ by 180°, the first-order reciprocating inertia forces F1 acting on the two cranks 11 are equal in magnitude and opposite in direction, and can cancel each other out. The two first-order reciprocating inertia forces F1 do not act on the same straight line, and an unbalanced moment M1 is generated in the horizontal plane xoz where the first direction X and the third direction Z are located, causing the mirror engine to rotate around the second direction Y, and every time the crankshaft 10 rotates 180°, the magnitude of M1 changes, and the direction is periodically switched to the opposite direction, causing the entire mirror engine to vibrate.

[0094] The moment elimination mass block 31 reciprocates along the first direction X driven by the crankshaft 10, and generates a first-order reciprocating inertia force F2 acting on the engine body. Two moment elimination devices 30 are installed on the crankshaft 10 at intervals, and the two first-order reciprocating inertia forces F2 do not act on the same straight line, thereby generating an unbalanced moment M2 in the horizontal plane xoz where the first direction X and the third direction Z are located. The directions of M1 and M2 are opposite, which can reduce or offset the vibration of the single unbalanced moment M1, significantly improve the NVH performance of the mirror engine, reduce the energy loss caused by vibration and unbalanced force, facilitate the mirror engine to work more efficiently, and the output power is more stable, which improves the overall performance and durability of the mirror engine.

[0095] Specifically, the inertia moment generated by the moment-eliminating mass block 31 is opposite in direction and equal in magnitude to the inertia moment generated by all the connecting rod transmission mechanisms 20, thereby eliminating the inertia moment generated by the connecting rod transmission mechanisms 20 and completely eliminating vibration. Optionally, the displacement magnitude of the moment-eliminating mass block 31 is the same as the displacement magnitude of the power piston 24, which is conducive to simplifying the inertia moment balance calculation of the torque elimination device 30 and the connecting rod transmission mechanism 20. For example, the phase angle of the displacement expression of the moment-eliminating mass block 31 and the displacement expression of the power piston 24 differs by 180°, and the other parameters are the same, thereby achieving equal magnitude, opposite direction, and being on the same plane, which greatly simplifies the selection of the moment-eliminating mass block 31.

[0096] The mirror engine provided in the present application can be a horizontal mirror engine or a vertical mirror engine, which is not specifically limited here. The number of cylinders of the mirror engine can be two (i.e., a single connecting rod transmission mechanism 20), four cylinders (i.e., two connecting rod transmission mechanisms 20) and multiple cylinders (i.e., multiple connecting rod transmission mechanisms 20), which is not specifically limited here. The mirror engine can be used as an engine for a range extender system, such as a range extender for an extended-range electric vehicle, an extended-range aircraft, an extended-range surface / underwater vehicle, an amphibious vehicle, a ground effect vehicle, etc., which is not specifically limited here.

[0097] Based on this, in the mirror engine, the number of crankshafts 11 and the number of connecting rod transmission mechanisms 20 can be flexibly selected, and the torque elimination device 30 can flexibly select its own parameters according to the inertia torque. The concept of mirror symmetry and modular design of the engine is proposed, and the interchangeability of parts, superposition of cylinder numbers and flexible layout are realized. The types of engine parts are greatly reduced by 11% compared with conventional design methods, which provides a solid foundation for engine engineering, serial design and manufacturing, and can greatly reduce the difficulty of equipment model development and reduce R&D costs and time.

[0098] In some embodiments, the torque elimination device 30 is directly mounted on the crankshaft 10. On the one hand, it does not need to be installed on the crankshaft 10 through a transmission mechanism, which reduces additional components and structural complexity and avoids the introduction of new vibration sources due to the addition of additional components. On the second hand, the structure is more compact, which significantly reduces the overall volume and weight of the engine, helps to optimize the internal space layout of the mirror engine, is beneficial to improve the power density and overall performance of the mirror engine, and simplifies the structure and control system of the mirror engine. On the third hand, it acts more directly on the crankshaft 10, shortens the lever arm, and the force on the crankshaft 10 in its length direction (third direction Z) is more uniform. At the same time, it will not occupy the original assembly space of the connecting rod transmission mechanism 20, which is convenient for the connecting rod transmission mechanism 20 and the torque elimination device 30 to be installed and maintained separately, thereby improving the modular design of the mirror engine, reducing maintenance costs and time, and improving the reliability and availability of the engine.

[0099] In some embodiments, in combination Fig.13 , the torque elimination device 30 is installed at the end of the crankshaft 10. The middle space of the crankshaft 10 is a key area for power transmission and conversion. Maintaining the original design of the connecting rod transmission mechanism 20 is not conducive to ensuring the stability and reliability of the connecting rod transmission mechanism 20, ensuring the smoothness and efficiency of power transmission, and will affect the core performance of the engine. It can ensure that the mirror engine can still maintain the original efficiency and reliability after the introduction of the torque elimination device 30, and adapt to the original car or aircraft. The torque elimination device 30 is installed at the end of the crankshaft 10 as an independent module, making the design of the entire mirror engine more modular. When the torque elimination device 30 needs to be replaced or repaired, it can be done separately without disassembling the entire engine, thereby reducing maintenance costs and time. Since the torque elimination device 30 is installed independently of the connecting rod transmission mechanism 20, different models and specifications of torque elimination devices 30 can be selected according to actual needs to generate torques M2 of different sizes and directions to adapt to different engines and application scenarios.

[0100] In some embodiments, in combination Fig.13 The installation phase angle of the torque-eliminating slider 34 differs by 180° from the installation phase angle of the adjacent power slider 22, so that the inertia moment generated by the torque-eliminating mass block 31 and the inertia moment generated by the adjacent connecting rod transmission mechanism 20 are in opposite directions, thereby effectively offsetting or reducing the vibration caused by the reciprocating inertia force F1, and at the same time indicating the phase angle installation requirements of the torque-eliminating slider 34.

[0101] In some embodiments, in combination Fig.14The installation phase angle of the moment-eliminating slider 34 differs by 180° from the installation phase angle of the adjacent power slider 22, so that the inertia force F2 generated by the moment-eliminating mass block 31 and the inertia force F1 generated by the adjacent connecting rod transmission mechanism 20 are in opposite directions, thereby effectively offsetting or reducing the vibration caused by the reciprocating inertia force F1, and at the same time indicating the phase angle installation requirements of the moment-eliminating slider 34. The inertia moments generated by the two moment-eliminating mass blocks 31 are in opposite directions, equal in magnitude, and on the same plane, achieving inertia moment balance.

[0102] In some embodiments, in combination Fig.13 The structure of each connecting rod transmission mechanism 20 is the same. On the one hand, it reduces the types of components and the difficulty of installation, improves the symmetry and mirroring of the mirror engine, and enables the inertial forces generated to balance each other through a phase difference of 180°; on the other hand, it is conducive to stable power output.

[0103] In some embodiments, in combination Fig.13 The number of connecting rod transmission mechanisms 20 is an even number, and each connecting rod transmission mechanism 20 is installed on a crank 11, which is beneficial to the smooth movement of the crankshaft 10 and the uniform distribution of the connecting rod transmission mechanism 20 in the length direction of the crankshaft 10, so that the engine has better symmetry in structure.

[0104] Specifically, the crankshaft 10 is evenly spaced along the length of the crankshaft 10, and the phase angles of two adjacent crankshafts 11 differ by 180°. Therefore, after the connecting rod transmission mechanism 20 is assembled on the crankshaft 11, the directions of the inertial forces generated by the two adjacent connecting rod transmission mechanisms 20 are opposite, which is beneficial to the reduction or balance of the inertial force.

[0105] Specifically, combined Fig.13 , the structures of the connecting rod transmission mechanisms 20 are the same, the inertial forces generated by each connecting rod transmission mechanism 20 are the same, and the phase angles differ by 180°, so the inertial forces generated by each pair of connecting rod transmission mechanisms 20 are balanced. Fig.13 In the two connecting rod transmission mechanisms 20, the direction of F1 generated by one connecting rod transmission mechanism 20 is toward the negative direction of the first direction X, and the direction of F1 generated by the other connecting rod transmission mechanism 20 is toward the positive direction of the first direction X, thereby achieving phase balance.

[0106] It can be understood that in other embodiments, the inertial force generated by all the connecting rod transmission mechanisms 20 is unbalanced, and the torque elimination device 30 generates an inertial force that is balanced therewith. For example, the structures of the connecting rod transmission mechanisms 20 are not necessarily all the same, or the phase angles of the connecting rod transmission mechanisms 20 are not necessarily opposite to each other. The combined inertial force generated by all the connecting rod transmission mechanisms 20 is an inertial force F1 in the negative direction of the first direction X. One torque elimination device 30 can be used to generate an inertial force F2 in the positive direction of the first direction X, and F1 and F2 are in opposite directions and equal in magnitude to achieve balance; two torque elimination devices 30 can also be used to generate an inertial force F2 in the positive direction of the first direction X, respectively, and F2 = 1 / 2*F1, to achieve inertial force balance.

[0107] In one embodiment, in combination Fig.13 There are two torque elimination devices 30, which are installed at intervals on the crankshaft 10. The inertial forces generated by the two torque elimination devices 30 are balanced, reducing stress concentration and vibration of engine components, thereby improving the operating stability of the engine.

[0108] In one embodiment, the inertia moment generated by all the connecting rod transmission mechanisms 20 is balanced with the inertia moment generated by the two torque elimination devices 30, the vibration and noise generated by the engine during operation will be greatly reduced, the stress and wear of the components will be reduced, and the overall life of the engine will be extended.

[0109] In some embodiments, in combination Fig.14 , the number of connecting rod transmission mechanisms 20 is an odd number, and each connecting rod transmission mechanism 20 is installed on a crank 11. The number of torque elimination devices 30 is two, and the two torque elimination devices 30 are installed on the crankshaft 10 at intervals. The inertia force generated by the two torque elimination devices 30 is balanced with the inertia force generated by all the connecting rod transmission mechanisms 20, and the directions of the inertia forces generated by the two torque elimination devices 30 are the same. The inertia moments generated by the two torque elimination devices 30 are balanced.

[0110] For example, combined with Fig.14 A connecting rod transmission mechanism 20 generates an inertia force F1 in the negative direction of the first direction X, and two torque elimination devices 30 generate an inertia force F2 in the positive direction of the first direction X, F2 = 1 / 2*F1, achieving inertia force balance without generating reciprocating inertia torque.

[0111] In some embodiments, in combination Figures 15 to 17The torque elimination device 30 also includes a first rotating wheel 32, a second rotating wheel 33 and a torque elimination slider 34. The first rotating wheel 32 is installed on the crankshaft 10, and the second rotating wheel 33 is linked with the first rotating wheel 32. The torque elimination slider 34 is rotatably eccentrically arranged on the second rotating wheel 33. The torque elimination slider 34 is slidably installed on the torque elimination mass block 31 along the second direction Y, so that the rotational motion of the eccentric position of the second rotating wheel 33 is divided into a linear reciprocating motion of the torque elimination slider 34 and the torque elimination mass block 31, and the linear motion conforms to the standard sine motion / cosine motion. The torque elimination mass block 31 will not generate second-order reciprocating inertia force, thereby reducing vibration and noise.

[0112] In one embodiment, the moment-eliminating mass block 31 has a second sliding groove 311 extending along the second direction Y, and the moment-eliminating slider 34 is slidably disposed in the second sliding groove 311. The second sliding groove 311 limits the moment-eliminating slider 34 to reliably slide along the second direction Y, and then the moment-eliminating mass blocks 31 divided in parallel can reliably slide along the first direction X, and both conform to standard sine motion / cosine motion.

[0113] In one embodiment, in combination Fig.18 and Fig.19 The moment-eliminating slider 34 is connected to a moment-eliminating pin 35, which is rotatably and eccentrically arranged on the second rotating wheel 33 through a moment-eliminating bearing 36. The arrangement of the moment-eliminating pin 35 enables the moment-eliminating slider 34 to realize eccentric motion, and its slider track 341 is circular. The moment-eliminating bearing 36 allows the moment-eliminating slider 34 to rotate relative to the second rotating wheel 33, so that the unbalanced torque in the system can be adjusted and balanced more flexibly, while reducing the friction and resistance between the moment-eliminating slider 34 and the second rotating wheel 33, thereby improving the efficiency of power transmission.

[0114] In one embodiment, in combination Fig.13 and Fig.14 The moment-eliminating slider 34 performs linear reciprocating motion on the moment-eliminating mass block 31 , and there is sliding friction between the two. The moment-eliminating slider 34 receives the thrust in the first direction X transmitted to the moment-eliminating mass block 31 .

[0115] In some embodiments, the transmission ratio between the first rotating wheel 32 and the second rotating wheel 33 is 1:1, so that the rotation speed of the second rotating wheel 33 is consistent with that of the crankshaft 10 .

[0116] In one embodiment, in combination Fig.15 The first rotating wheel 32 and the second rotating wheel 33 are connected by a synchronous belt 371, and the transmission ratio is accurate, which reduces the vibration and noise caused by the transmission error.

[0117] In one embodiment, in combination Fig.16 and Fig.17The first rotating wheel 32 and the second rotating wheel 33 are meshed and connected, with accurate transmission ratio, good stability and high reliability. The gear transmission can withstand large torque and load, thereby improving the operating stability of the torque elimination device 30.

[0118] Optionally, the first rotating wheel 32 and the second rotating wheel 33 are directly meshed, reducing the number of intermediate components. Fig.17 The first rotating wheel 32 and the second rotating wheel 33 are meshed through the transmission gear 372 to achieve the same rotation direction.

[0119] In one embodiment, the first rotating wheel 32 and the second rotating wheel 33 are connected by a synchronous chain, which has high transmission reliability and can transmit greater power and torque.

[0120] The synchronous belt 371, the first rotating wheel 32 and the second rotating wheel 33 are directly meshed, and the synchronous chain has the functions of synchronous belt timing, gear timing and chain timing respectively, ensuring that the inertia force or inertia moment generated by the torque elimination device 30 is opposite in direction and equal in magnitude to the inertia force or inertia moment generated by all Scotch yoke transmission mechanisms, thereby reducing the vibration of the engine.

[0121] In some embodiments, in combination Fig.13 The torque elimination device 30 further includes a torque elimination guide rail 38, which extends along the first direction X. The torque elimination mass block 31 can be movably mounted on the torque elimination guide rail 38 along the torque elimination guide rail 38. The torque elimination guide rail 38 limits the moment elimination mass block 31 to perform linear reciprocating motion in the first direction X, and the direction of the inertial force and inertial moment generated by it can be controlled, thereby ensuring that the unbalanced torque can be quickly responded to and eliminated, thereby improving the stability of the engine.

[0122] In one embodiment, in combination Fig.13 The moment-eliminating mass block 31 is rollingly mounted on the moment-eliminating guide rail 38 through the rolling body 39, which reduces the moving friction of the moment-eliminating mass block 31, reduces the friction resistance and wear that may be generated by sliding friction, and improves the movement stability of the system.

[0123] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions and improvements made within the spirit and principles of the present invention should be included in the protection scope of the present invention.

Claims

1. A connecting rod transmission mechanism, characterized in that: The connecting rod transmission mechanism includes a power slider, a power connecting rod and two power pistons. The power connecting rod includes a connecting rod base and two straight rod portions. The straight rod portions extend along a first direction. The front end portion of each straight rod portion is connected to one of the power pistons. The rear end portion of the straight rod portion is fixedly connected to the connecting rod base. The two straight rod portions are located on opposite sides of the connecting rod base in the first direction. The power slider is slidably mounted on the connecting rod base in a second direction. The first direction is perpendicular to the second direction.

2. The connecting rod transmission mechanism according to claim 1, characterized in that: The rear end portion is connected to the connecting rod base body by a rounded transition.

3. The connecting rod transmission mechanism according to claim 1, characterized in that: An engine equipped with the connecting rod transmission mechanism has a high compression ratio.

4. The connecting rod transmission mechanism according to claim 1, characterized in that: The dimension of the straight rod portion in the third direction is close to the dimension of the connecting rod base in the third direction.

5. The connecting rod transmission mechanism according to claim 1, characterized in that: The straight rod portion and the connecting rod base are integrally formed; or, the straight rod portion and the connecting rod base are welded, threaded, interference-fitted or fastened.

6. The connecting rod transmission mechanism according to claim 1, characterized in that: The connecting rod base has a first sliding groove extending along the second direction inside, and the power sliding block is slidably disposed in the first sliding groove.

7. The connecting rod transmission mechanism according to claim 6, characterized in that: The groove wall of the first sliding groove has a linear guide rail, and the power sliding block is slidably arranged on the linear guide rail.

8. The connecting rod transmission mechanism according to claim 1, characterized in that: The cross-sectional shape of the connecting rod base and / or the straight rod portion perpendicular to the first direction is a W-shape, an I-shape, a quadrilateral, a circle, an ellipse, a circular ring or an elliptical ring.

9. The connecting rod transmission mechanism according to any one of claims 1 to 8, characterized in that: The connecting rod transmission mechanism further comprises a power bearing, which is installed in the power slider through the power bearing; the middle of the power bearing has an oil hole; And / or, the connecting rod transmission mechanism also includes a piston pin and two retaining rings, the front end portion of the straight rod portion has a through pin hole, the two ends of the power piston respectively have retaining grooves, the two retaining rings are respectively engaged in the two retaining grooves, the piston pin is inserted into the pin hole, and the two ends of the piston pin respectively abut against the two retaining rings.

10. A mirror image engine, characterized in that: The mirror engine comprises a crankshaft, a torque elimination device, two cylinders and a connecting rod transmission mechanism according to any one of claims 1 to 9, wherein the length direction of the crankshaft is consistent with a third direction, the crankshaft rotates around the third direction, and the crankshaft comprises at least one crank throw; the first direction, the second direction and the third direction are perpendicular to each other; The power slider is rotatably mounted on the crank, and each power piston is slidably disposed in one of the cylinders along the first direction; The torque elimination device includes a torque elimination mass block, which reciprocates along the first direction under the drive of the crankshaft. The inertia torque generated by the torque elimination mass block acting on the engine body is opposite to the inertia torque generated by all the connecting rod transmission mechanisms acting on the engine body.

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