Opposed engine

Abstract

The invention relates to the technical field of engines, and provides an opposed engine, comprising a crankshaft, a power unit and a torque elimination device. The crankshaft rotates about a third direction, the power unit comprises a Scotch yoke transmission mechanism and two cylinders, the Scotch yoke transmission mechanism comprises a power slider, a power connecting rod and two power pistons, the power slider is rotatably mounted on the crank, the power slider is slidably mounted on the power connecting rod along a second direction, the two power pistons are respectively mounted on the two ends of the power connecting rod in a first direction, and each power piston is slidably arranged in a corresponding cylinder along the first direction; the torque elimination mass block of the torque elimination device performs reciprocating linear motion along the first direction under the drive of the crankshaft, the inertia moment generated by the torque elimination mass block acting on the engine body is opposite in direction to the inertia moment generated by all Scotch yoke transmission mechanisms acting on the engine body, effectively offsetting or reducing the inertia moment of the Scotch yoke transmission mechanism, and significantly improving NVH performance.

Description

Technical Field

[0001] The present invention relates to the technical field of engines, and in particular to an opposed engine. Background Art

[0002] Traditional engines that use a crank-connecting rod mechanism will generate first-order and second-order reciprocating inertia moments when working, causing engine vibrations. This not only consumes energy and affects the normal operation of the engine, but can also cause engine resonance in severe cases, reducing the engine's NVH (Noise, Vibration, Harshness) performance. Summary of the invention

[0003] The purpose of the present invention is to provide an opposed engine, aiming to solve the technical problem that the NVH performance of existing engines needs to be improved.

[0004] The present application provides an opposed engine, wherein the opposed engine has a first direction, a second direction and a third direction which are perpendicular to each other, the opposed engine comprises a crankshaft, a power unit and a torque elimination device, the length direction of the crankshaft is consistent with the third direction, the crankshaft rotates around the third direction, and the crankshaft comprises at least one crank throw;

[0005] The power unit comprises a Scotch yoke transmission mechanism and two cylinders, the Scotch yoke transmission mechanism comprises a power slider, a power connecting rod and two power pistons, the power slider is rotatably mounted on the crank, the power slider is slidably mounted on the power connecting rod along the second direction, the two power pistons are respectively mounted on the two ends of the power connecting rod in the first direction, and each power piston is slidably arranged on the corresponding cylinder along the first direction;

[0006] The torque elimination device includes a torque elimination mass block, which performs reciprocating linear motion 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 Scotch yoke transmission mechanisms acting on the engine body.

[0007] In one embodiment, the torque elimination device is mounted on the end of the crankshaft.

[0008] In one of the embodiments, the installation phase angle of the torque elimination slider of the torque elimination device differs by 180° from the installation phase angle of the adjacent power slider.

[0009] In one embodiment, the number of the power units is an even number, and each of the power units is installed on one of the crankshafts.

[0010] In one embodiment, the inertial forces generated by all the power units are balanced;

[0011] In one embodiment, the number of the torque elimination devices is two, and the two torque elimination devices are installed on the crankshaft at intervals, and the inertial forces generated by the two torque elimination devices are balanced.

[0012] In one embodiment, the inertia moments generated by all the power units are balanced with the inertia moments generated by the two torque elimination devices.

[0013] In one embodiment, the number of the power units is an odd number, and each of the power units is installed on one of the crankshafts; the number of the torque elimination devices is two, and the two torque elimination devices are installed on the crankshaft at intervals, the inertia force generated by the two torque elimination devices is balanced with the inertia force generated by all the power units, and the directions of the inertia forces generated by the two torque elimination devices are the same; the inertia moments generated by the two torque elimination devices are balanced.

[0014] In one embodiment, the torque elimination device also includes a first rotating wheel, a second rotating wheel and a torque elimination slider, the first rotating wheel is mounted on the crankshaft, the second rotating wheel is linked to the first rotating wheel, the torque elimination slider is rotatably eccentrically arranged on the second rotating wheel, and the torque elimination slider is slidably mounted on the torque elimination mass block along the second direction.

[0015] In one of the embodiments, the torque-eliminating mass block has a first sliding groove extending along the second direction, and the torque-eliminating sliding block is slidably disposed in the first sliding groove.

[0016] In one of the embodiments, the torque-eliminating slider is connected to a torque-eliminating pin, and the torque-eliminating pin is rotatably eccentrically disposed on the second rotating wheel via a torque-eliminating bearing.

[0017] In one embodiment, the first rotating wheel and the second rotating wheel are connected by a synchronous belt.

[0018] In one embodiment, the first rotating wheel and the second rotating wheel are meshingly connected.

[0019] In one embodiment, the first rotating wheel and the second rotating wheel are connected by a synchronous chain.

[0020] In one of the embodiments, the torque elimination device further comprises a guide rail extending along the first direction, and the torque elimination mass block is movably mounted on the guide rail along the guide rail.

[0021] In one of the embodiments, the moment-eliminating mass block is rollingly mounted on the guide rail via rolling bodies.

[0022] The opposed engine provided by the present invention has the following beneficial effects: the power unit adopts a Scotch Yoke transmission mechanism, the power slider performs reciprocating linear motion along the second direction relative to the power connecting rod, and the power connecting rod performs reciprocating linear motion along the first direction, and the combined motion of the two makes the reciprocating linear motion of the power piston conform to the standard sine motion or cosine motion law relative to the crankshaft rotation angular displacement, and the speed of the power piston is slow at the outer / top dead center position, which is beneficial to improving the combustion quality; the power slider, the power connecting rod and the power piston are reciprocating linear motion components, and the Scotch Yoke transmission mechanism only generates a first-order reciprocating inertia force, and does not generate a second-order reciprocating inertia force, which reduces the Vibration and noise; the torque elimination mass block of the torque elimination device also performs reciprocating linear motion, and the inertia moment generated by the torque elimination mass block is opposite to the inertia moment generated by the Scotch yoke transmission mechanism and is on the same plane, effectively offsetting or reducing the inertia moment of the Scotch yoke transmission mechanism, significantly improving the NVH performance of the opposed engine, solving the technical problem that the NVH performance of the existing engine needs to be improved, reducing the energy loss caused by vibration and unbalanced force, and facilitating the opposed engine to work more efficiently, with a more stable output power, thereby improving the overall performance and durability of the opposed engine. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] 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.

[0024] Figure 1 A schematic diagram of the structure of an opposed engine provided by an embodiment of the present invention;

[0025] Figure 2 for Figure 1 A schematic diagram of the structure of the Scotch yoke transmission mechanism of the opposed engine;

[0026] Figure 3 Schematic diagram for comparing the displacement of a power piston and a conventional piston;

[0027] Figure 4 A schematic diagram showing the speed comparison between the power piston and the conventional piston;

[0028] Figure 5 It is a schematic diagram comparing the acceleration of the power piston and the traditional piston;

[0029] Figure 6 A schematic diagram comparing the jerkiness of a power piston and a conventional piston;

[0030] Figure 7 for Figure 1 A first structural schematic diagram of a torque elimination device for an opposed engine;

[0031] Figure 8 for Figure 1 A second structural schematic diagram of the torque elimination device of the opposed engine;

[0032] Fig. 9 for Figure 1 A third structural schematic diagram of the torque elimination device of the opposed engine;

[0033] Fig.10 for Figure 1 A schematic diagram of the assembly of the second rotating wheel and the torque elimination pin of the torque elimination device;

[0034] Fig.11 for Fig.10 Right sectional view of;

[0035] Fig.12 A schematic diagram of another structure of the opposed engine provided in this embodiment;

[0036] Fig.13 for Fig.12 Schematic diagram of the improved structure of the opposed engine in FIG.

[0037] Fig.14 Schematic diagram of lubrication design of the torque elimination device provided in this embodiment.

[0038] Among them, the reference numerals in the figure are:

[0039] X, first direction; Y, second direction; Z, third direction;

[0040] 10. Crankshaft; 11. Crank; 12. Axis; 13. Rotation trajectory; 20. Power unit; 21. Cylinder; 22. Power slider; 23. Power connecting rod; 231. Second sliding groove; 24. Power piston; 25. Piston pin; 26. Power bearing; 30. Torque elimination device; 31. Torque elimination mass block; 311. First sliding groove; 312. Lubricating layer; 32. First rotating wheel; 33. Second rotating wheel; 34. Torque elimination slider; 341. Slider trajectory; 342. Third flow channel; 35. Torque elimination pin; 36. Torque elimination bearing; 361. Oil hole; 362. First flow channel; 363. Second flow channel; 364. First branch flow channel; 365. Second branch flow channel; 371. Synchronous belt; 372. Transmission gear; 38. Guide rail; 39. Rolling body. DETAILED DESCRIPTION

[0041] 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.

[0042] 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.

[0043] 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.

[0044] 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.

[0045] 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 directly connected or indirectly connected 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.

[0046] Please combine Figure 1 and Figure 2The present application provides an opposed engine. The opposed engine has a first direction X, a second direction Y and a third direction Z that are perpendicular to each other. The opposed engine includes a crankshaft 10, a power unit 20 and a torque elimination device 30. The length direction of the crankshaft 10 is consistent with the third direction Z, that is, the axis 12 of the crankshaft 10 is consistent with the third direction Z. The crankshaft 10 rotates around the third direction Z. The crankshaft 10 includes at least one crank throw 11. In other words, the number of crank throws 11 can be one (see Fig.13 ), two (see Figure 1 ), or more than two, without specific limitation here.

[0047] The power unit 20 includes a Scotch yoke transmission mechanism and two cylinders 21. The Scotch yoke transmission mechanism includes a power slider 22, a power connecting rod 23 and two power pistons 24. 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 power units 20. Each crank 11 may be equipped with a power unit 20, or some cranks 11 may be equipped with power units 20, and some cranks 11 are idle. Generally, the number of cranks 11 is equal to the number of power units 20, and they correspond one to one. The power slider 22 can be slidably mounted on the power connecting rod 23 along the second direction Y, and the two power pistons 24 are respectively mounted at the two ends of the power connecting rod 23 in the first direction X, and each power piston 24 can be slidably set in the corresponding cylinder 21 along the first direction X. Optionally, the power piston 24 is connected to the power connecting rod 23 through a piston pin 25.

[0048] The torque elimination device 30 includes a torque elimination mass block 31, which performs reciprocating linear motion 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 Scotch yoke transmission mechanisms acting on the engine body.

[0049] In a specific embodiment, in combination Figure 1The four-cylinder horizontal mirror-symmetrical engine includes two horizontally opposed symmetrical power units 20 and two torque elimination devices 30. Taking the power unit 20 close to the positive direction of the third direction Z as an example, the power slider 22 moves in a plane along the rotation trajectory 13 with the crank 11. 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 center of the power slider 22 to the axis 12, which is a constant; φ is the angle between the line connecting the power slider 22 to the axis 12 and the horizontal plane, or the rotation angle of the slider 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 reciprocating linear 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 to obtain the speed of the power piston 24 (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 power unit 20 that perform linear motion only generate first-order reciprocating inertia force, and no second-order reciprocating inertia force is generated.

[0050] 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. 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.

[0051] Further analysis combined with Figure 3 The reciprocating linear motion of the power piston 24 provided in the present application is pure cosine / sine motion relative to the rotational angular displacement of the crankshaft 10, which is convenient for achieving complete dynamic balance. The traditional piston is 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 energy consumption of the moving parts is lower, and more chemical energy is used for output torque. Figure 4The power piston 24 leaves the dead center position more slowly, which helps to expand the combustion flame front, facilitates full combustion, facilitates environmental emissions, and facilitates the full conversion of chemical energy into mechanical energy; the power piston 24 approaches the dead center position more slowly, which helps to prevent detonation and facilitates the use of low-grade fuel under the premise of high compression ratio. 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 The power piston 24 has a smaller and smoother impact, which helps the power unit 20 and the opposed engine to obtain better NVH performance.

[0052] Combination Figure 1 and Figure 2 For a four-cylinder horizontal mirror-symmetric 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 symmetrical 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 vibration of the entire symmetrical engine.

[0053] Please continue to see Figure 1 The torque elimination mass block 31 moves back and forth in a straight line along the first direction X driven by the crankshaft 10, and the torque elimination mass block 31 generates a first-order reciprocating inertia force F2 acting on the engine body. The two torque 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.

[0054] Specifically, the inertia moment generated by the moment-eliminating mass block 31 is opposite in direction to the inertia moment generated by all Scotch yoke transmission mechanisms, is equal in magnitude, and is on the same plane, thereby eliminating the inertia moment generated by the power unit 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 moment elimination device 30 and the power unit 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.

[0055] Based on this, in the present application, the power unit 20 adopts a Scotch Yoke transmission mechanism, the power slider 22 performs reciprocating linear motion along the second direction Y relative to the power connecting rod 23, and the power connecting rod 23 performs reciprocating linear motion along the first direction X relative to the crankshaft 10, which conforms to the standard sine motion or cosine motion law, and the power piston 24 has a slow speed at the outer / top dead center position, which is conducive to improving the combustion quality, sufficient combustion, good emission indicators and other characteristics. The power slider 22, the power connecting rod 23 and the power piston 24 are reciprocating linear motion components, and the Scotch Yoke transmission mechanism only generates a first-order reciprocating inertia force, and does not generate a second-order reciprocating inertia force, which reduces vibration and noise to a certain extent. The torque eliminating mass block 31 of the torque eliminating device 30 also performs reciprocating linear motion, and the inertia torque generated by the torque eliminating mass block 31 is opposite to the direction of the inertia torque generated by the Scotch yoke transmission mechanism, effectively offsetting or reducing the inertia torque of the Scotch yoke transmission mechanism, significantly improving the NVH performance of the opposed engine, reducing the energy loss caused by vibration and unbalanced force, and facilitating the opposed engine to work more efficiently, with a more stable output power, thereby improving the overall performance and durability of the opposed engine.

[0056] The opposed engine provided in the present application may be a horizontal mirror-symmetrical engine or a vertical mirror-symmetrical engine, which is not specifically limited here. The number of cylinders of the opposed engine may be two (i.e., a single power unit 20), four cylinders (i.e., two power units 20), and multiple cylinders (i.e., multiple power units 20), which is not specifically limited here. The opposed 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.

[0057] In this embodiment, the moment-eliminating mass block 31 performs reciprocating linear motion along the first direction X, and the required motion space is small, which is beneficial to greatly reduce the height of the opposed engine.

[0058] 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 opposed engine, is beneficial to improve the power density and overall performance of the opposed engine, and simplifies the structure and control system of the opposed 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 power unit 20, which is convenient for the power unit 20 and the torque elimination device 30 to be installed and maintained separately, thereby improving the modular design of the opposed engine, reducing maintenance costs and time, and improving the reliability and availability of the engine.

[0059] In some embodiments, in combination Figure 1 , 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 power unit 20 is not conducive to ensuring the stability and reliability of the power unit 20, ensuring the smoothness and efficiency of power transmission, and will affect the core performance of the engine. It can ensure that the opposed engine can still maintain the original efficiency and reliability after the introduction of the torque elimination device 30, and adapt to the original automobile 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 opposed 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 power unit 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.

[0060] In some embodiments, in combination Figure 1 and Fig.12 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 inertial force F2 generated by the torque-eliminating mass block 31 and the inertial force F1 generated by the adjacent power unit 20 are in opposite directions, thereby effectively offsetting or reducing the vibration caused by the reciprocating inertial force F1, and at the same time indicating the phase angle installation requirements of the torque-eliminating slider 34.

[0061] In some embodiments, in combination Figure 1 and Fig.13The 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 power unit 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.

[0062] In some embodiments, in combination Figure 2 The two cylinders 21 , the two power pistons 24 , and the power connecting rod 23 in the power unit 20 are symmetrically distributed about the center of the power slider 22 .

[0063] In some embodiments, in combination Figure 1 The structure of the power unit 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 opposed 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.

[0064] In some embodiments, in combination Figure 1 The number of the power units 20 is an even number, and each power unit 20 is installed on a crank 11, which is beneficial to the smooth movement of the crankshaft 10 and the uniform distribution of the power units 20 in the length direction of the crankshaft 10, so that the engine has better symmetry in structure.

[0065] Specifically, the cranks 11 are evenly spaced along the length of the crankshaft 10, and the phase angles of two adjacent cranks 11 differ by 180°. Therefore, after the power units 20 are assembled on the cranks 11, the directions of the inertial forces generated by the two adjacent power units 20 are opposite, which is beneficial to the reduction or balance of the inertial force.

[0066] Specifically, combined Figure 1 , the structures of the power units 20 are the same, the inertial forces generated by each power unit 20 are the same, and the phase angles differ by 180°, so the inertial forces generated by each pair of power units 20 are balanced. Figure 1 Among the two power units 20, the direction of F1 generated by one power unit 20 is toward the negative direction of the first direction X, and the direction of F1 generated by the other power unit 20 is toward the positive direction of the first direction X, so as to achieve phase balance.

[0067] It can be understood that in other embodiments, the inertial force generated by all power units 20 is unbalanced, and the torque elimination device 30 generates an inertial force that is balanced therewith. For example, the structures of the power units 20 are not necessarily all the same, or the phase angles of the power units 20 are not necessarily opposite to each other. The combined inertial force generated by all power units 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 inertial forces F2 in the positive direction of the first direction X, respectively, and F2 = 1 / 2*F1, to achieve inertial force balance.

[0068] In one embodiment, in combination Figure 1 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 internal components of the engine, thereby improving the operating stability of the engine.

[0069] In one embodiment, the inertia moment generated by all power units 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.

[0070] In some embodiments, in combination Fig.13 , the number of power units 20 is an odd number, and each power unit 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 power units 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.

[0071] For example, combined with Fig.12 , a power unit 20 generates an inertia force F1 in the negative direction of the first direction X, and a torque elimination device 30 generates an inertia force F2 in the positive direction of the first direction X. F1 and F2 are in opposite directions and equal in magnitude to achieve balance, but F1 and F2 are not collinear, forming a reciprocating inertia moment, which still causes vibration of the engine. For this reason, combined with Fig.13 A power unit 20 generates an inertial force F1 in the negative direction of the first direction X, and two torque elimination devices 30 generate an inertial force F2 in the positive direction of the first direction X, F2 = 1 / 2*F1, achieving inertial force balance without generating reciprocating inertial torque.

[0072] In some embodiments, in combination Figures 7 to 9The 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 the reciprocating linear 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.

[0073] In one embodiment, the moment-eliminating mass block 31 has a first sliding groove 311 extending along the second direction Y, and the moment-eliminating slider 34 is slidably disposed in the first sliding groove 311. The first 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.

[0074] In one embodiment, in combination Fig.10 and Fig.11 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.

[0075] In one embodiment, in combination Figure 7 and Fig.14 The torque-eliminating slider 34 makes a reciprocating linear motion on the torque-eliminating mass block 31, and there is sliding friction between the two. The torque-eliminating slider 34 bears the thrust in the first direction X transmitted to the torque-eliminating mass block 31. In the ignition / power stroke, the thrust in the first direction X is large. For this reason, a lubricating layer 312 is provided between the torque-eliminating slider 34 and the torque-eliminating mass block 31 to realize dynamic pressure lubrication or elastohydrodynamic lubrication, so as to reduce friction and wear, thereby improving the overall efficiency and service life of the engine.

[0076] Specifically, the torque-eliminating slider 34 is sleeved with the torque-eliminating pin 35 through the torque-eliminating bearing 36. The middle part of the torque-eliminating bearing 36 has an oil hole 361. The torque-eliminating bearing 36 has a first flow channel 362 distributed in the radial direction and a second flow channel 363 distributed along the circumferential direction of the surface. The first flow channel 362 distributed in the radial direction is connected with the oil hole 361. The first flow channel 362 distributed in the radial direction and the second flow channel 363 distributed along the circumferential direction of the surface are at least partially connected. The first flow channel 362 guides the lubricating fluid flowing out of the oil hole 361 to flow to the second flow channel 363 on the surface of the torque-eliminating bearing 36, so as to achieve a dynamic pressure lubrication effect.

[0077] Specifically, the torque-eliminating slider 34 has a third flow channel 342, and the third flow channel 342 is connected to the second flow channel 363 and the lubricating layer 312 respectively. When the torque-eliminating bearing 36 rotates, the second flow channel 363 guides the flow of lubricating fluid, establishes a stable lubricating layer 312, provides sufficient lubricating oil, and realizes reliable lubrication, thereby avoiding the possibility of rupture of the lubricating oil film and causing direct contact of the rough peaks. The lubricating oil further flows to the lubricating layer 312 through the third flow channel 342, so that the lubricating fluid overflowing from the third flow channel 342 and flowing out of the surface of the torque-eliminating slider 34 can be quickly spread on the surface of the friction pair, especially the distal area away from the oil hole 361, thereby reducing the friction and wear between the torque-eliminating slider 34 and the torque-eliminating mass block 31. Based on this, since the third flow channel 342 can supply sufficient lubricating oil, there is no need to open a large-sized oil groove on the surface of the torque-eliminating slider 34, thereby avoiding reducing the structural strength of the torque-eliminating slider 34 and also avoiding causing the surface roughness of the torque-eliminating slider 34 to be too large.

[0078] Optionally, the moment-eliminating mass block 31 performs reciprocating linear motion, and the friction pair between the moment-eliminating slider 34 and the moment-eliminating mass block 31 changes back and forth with the sliding direction, and the load changes dramatically. Based on the sine motion / cosine motion law of the moment-eliminating mass block 31, the moment-eliminating slider 34 and the moment-eliminating mass block 31 are only subjected to force on one side at the same time, that is, at the same time, only one side of the moment-eliminating slider 34 and the inner surface of the moment-eliminating mass block 31 are in close contact to form a friction pair. In one rotation cycle, the two friction surfaces alternately form a friction pair with the moment-eliminating mass block 31, that is, any friction surface on the moment-eliminating slider 34 is not constant as a friction pair. This alternating characteristic causes the lubricating layer 312 to quickly rupture and fail due to the increase in the gap between the friction pairs when the friction pair is detached, and the gap is in an oil-poor state. When the friction pair is formed again by pairing, the friction lubrication will be greatly affected due to insufficient oil supply.

[0079] To this end, the second flow channel 363 is fixed to the torque-eliminating slider 34 and does not rotate. Therefore, it is only necessary to set the second flow channels 363 on both sides of the torque-eliminating bearing 36 in the first direction X, and both are connected to the third flow channel 342, corresponding to the friction of the torque-eliminating slider 34 and the torque-eliminating mass block 31 on different sides. The first flow channel distributed along the radial direction rotates synchronously with the second rotating wheel 33, and continuously rotates and changes. In accordance with the rotation law of the second rotating wheel 33, when the torque-eliminating mass block 31 moves in the positive direction of the first direction X, the first flow channel 362 circulates with the second flow channel 363 close to the positive direction of the first direction X, but is not connected with the second flow channel 363 close to the negative direction of the first direction X, so that the lubricating oil is concentratedly supplied to the side of the torque-eliminating slider 34 and the torque-eliminating mass block 31 where friction is occurring. When the moment-eliminating mass block 31 moves in the negative direction along the first direction X, the first flow channel 362 flows with the second flow channel 363 close to the negative direction of the first direction X, but is not connected with the second flow channel 363 close to the positive direction of the first direction X, so that the lubricating oil is concentratedly supplied to the side of the moment-eliminating slider 34 and the moment-eliminating mass block 31 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.

[0080] Optionally, the inner ring of the moment-eliminating bearing 36 is fixedly connected to the moment-eliminating pin 35, that is, the moment-eliminating pin 35 is fixed to a part of the hole wall of the oil hole 361, and a gap is provided between another part of the hole wall of the oil hole 361 and the moment-eliminating pin 35, so that lubricating oil can flow into the first flow channel 362. The outer ring of the moment-eliminating bearing 36 is fixedly connected to the moment-eliminating slider 34. The second flow channel 363 includes a first branch flow channel 364 and a second branch flow channel 365, which are respectively located on opposite sides of the outer ring of the dynamic bearing 26 in the first direction X. The first branch flow channel 364 is located in the negative direction of the first direction X compared to the second branch flow channel 365. The first branch flow channel 364 and the second branch flow channel 365 are always connected to the third flow channel 342. The inner ring of the moment-eliminating bearing 36 rotates synchronously with the moment-eliminating pin 35 relative to the outer ring. When the moment-eliminating mass block 31 slides in the negative direction along the first direction X, the first flow channel 362 is connected to the first branch flow channel 364 and disconnected from the second branch flow channel 365; when the moment-eliminating mass block 31 slides in the positive direction along the first direction X, the first flow channel 362 is connected to the second branch flow channel 365 and disconnected from the first branch flow channel 364. Based on this, in accordance with the sinusoidal motion law of the moment-eliminating mass block 31, the first flow channel 362 is alternately connected to the first branch flow channel 364 and the second branch flow channel 365, so that the lubricating oil is concentratedly supplied to the side of the moment-eliminating slider 34 and the moment-eliminating mass block 31 where friction is occurring, so as to realize the targeted supply of lubricating oil. The supply of lubricating oil is increased on the side of the friction pair, effectively reducing friction and wear. While ensuring reliable lubrication, excessive pump oil loss and reduced efficiency are avoided.

[0081] 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 .

[0082] In one embodiment, in combination Figure 7 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.

[0083] In one embodiment, in combination Figure 8 and Fig. 9 The 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.

[0084] Optionally, the first rotating wheel 32 and the second rotating wheel 33 are directly meshed, reducing the intermediate components. Optionally, the first rotating wheel 32 and the second rotating wheel 33 are meshed through the transmission gear 372, so that the two rotate in the same direction.

[0085] 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.

[0086] 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.

[0087] In some embodiments, in combination Figure 7 The torque elimination device 30 further includes a guide rail 38, which extends along the first direction X. The torque elimination mass block 31 is movably mounted on the guide rail 38 along the guide rail 38. The guide rail 38 limits the moment elimination mass block 31 to make reciprocating linear 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.

[0088] In one embodiment, in combination Figures 7 to 9 The moment-eliminating mass block 31 is rollingly mounted on the 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.

[0089] In some embodiments, in combination Figure 1 and Figure 2The power slider 22 has a second sliding groove 231 extending along the second direction Y, and the power slider 22 is slidably disposed in the second sliding groove 231. The second sliding groove 231 limits the power slider 22 to slide reliably along the second direction Y. The power slider 22 performs reciprocating linear motion along the first direction X under the drive of the crankshaft 10, and then the combined crank 11 rotates around the third direction Z.

[0090] 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 reciprocating linear motion along the first direction X and reciprocating linear motion along the second direction Y in the second sliding groove 231. 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 reciprocating swing around the piston pin 25, thereby improving the efficiency of power transmission.

[0091] The above are only preferred embodiments of the present invention and are 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. An opposed engine, characterized in that: The opposed engine has a first direction, a second direction and a third direction which are perpendicular to each other, and comprises a crankshaft, a power unit and a torque elimination device, wherein the length direction of the crankshaft is consistent with the third direction, the crankshaft rotates around the third direction, and the crankshaft comprises at least one crank throw; The power unit comprises a Scotch yoke transmission mechanism and two cylinders, the Scotch yoke transmission mechanism comprises a power slider, a power connecting rod and two power pistons, the power slider is rotatably mounted on the crank, the power slider is slidably mounted on the power connecting rod along the second direction, the two power pistons are respectively mounted on the two ends of the power connecting rod in the first direction, and each power piston is slidably arranged on the corresponding cylinder along the first direction; The torque elimination device includes a torque elimination mass block, which performs reciprocating linear motion 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 Scotch yoke transmission mechanisms acting on the engine body.

2. The opposed engine according to claim 1, characterized in that: The torque elimination device is installed at the end of the crankshaft; the installation phase angle of the torque elimination slider of the torque elimination device is 180° different from the installation phase angle of the adjacent power slider.

3. The opposed engine according to claim 1, characterized in that: The number of the power units is an even number, and each of the power units is installed on one of the crankshafts; the inertial forces generated by all the power units are balanced; There are two torque elimination devices, which are installed on the crankshaft at intervals, and the inertia forces generated by the two torque elimination devices are balanced; The inertia moments generated by all the power units are balanced with the inertia moments generated by the two torque elimination devices.

4. The opposed engine according to claim 1, characterized in that: The number of the power units is an odd number, and each of the power units is installed on one of the cranks; There are two torque elimination devices, which are installed on the crankshaft at intervals, and the inertia force generated by the two torque elimination devices is balanced with the inertia force generated by all the power units, and the directions of the inertia forces generated by the two torque elimination devices are the same; The inertia moments generated by the two moment elimination devices are balanced.

5. The opposed engine according to claim 1, characterized in that: The torque elimination device also includes a first rotating wheel, a second rotating wheel and a torque elimination slider. The first rotating wheel is installed on the crankshaft, the second rotating wheel is linked to the first rotating wheel, the torque elimination slider is rotatably eccentrically arranged on the second rotating wheel, and the torque elimination slider is slidably installed on the torque elimination mass block along the second direction.

6. The opposed engine according to claim 5, characterized in that: The moment-eliminating mass block has a first sliding groove extending along the second direction, and the moment-eliminating sliding block is slidably disposed in the first sliding groove.

7. The opposed engine according to claim 5, characterized in that: The torque-eliminating slider is connected with a torque-eliminating pin, and the torque-eliminating pin is rotatably eccentrically arranged on the second rotating wheel through a torque-eliminating bearing.

8. The opposed engine according to claim 5, characterized in that: The torque elimination device also includes one of the following: The first rotating wheel and the second rotating wheel are connected by a synchronous belt; The first rotating wheel and the second rotating wheel are meshed and connected; The first rotating wheel and the second rotating wheel are connected by a synchronous chain.

9. The opposed engine according to any one of claims 1 to 8, characterized in that: The torque elimination device further comprises a guide rail extending along the first direction, and the torque elimination mass block is movably mounted on the guide rail along the guide rail.

10. The opposed engine according to claim 9, characterized in that: The moment-eliminating mass block is rollingly mounted on the guide rail via a rolling body.

Images