V-shaped engine

Abstract

The invention provides a V-shaped engine, and relates to the technical field of engines and new energy automobiles. The crankshaft is arranged on the machine body; each driving assembly comprises an air cylinder arranged above the machine body and a driving assembly arranged above the machine body. One end of the connecting rod is connected to the crankshaft; the piston is connected to the other end of the connecting rod; the crankshaft drives the balance assembly to act through the transmission mechanism, the balance assembly is constructed to respond to inertia force generated in the air cylinder due to the alternate reciprocating motion of the two pistons and acting on the crankshaft, and lateral force suitable for counteracting at least one part of the inertia force is provided for the crankshaft through the transmission mechanism so as to reduce vibration of the machine body.

Description

Technical Field

[0001] This disclosure relates to the technical fields of engines and new energy vehicles, and more specifically, to a V-type engine. Background Technology

[0002] Range-extended electric vehicles (REEVs) represent an important technological route for new energy vehicles. The range extender is a crucial component of a REEV; its function is to convert the vehicle's internal fuel into mechanical energy output by the engine, according to instructions from the vehicle controller. This mechanical energy is then further converted into electrical energy by a generator, ultimately increasing the electric vehicle's driving range.

[0003] In recent years, with the gradual improvement of charging infrastructure, range-extended electric vehicles have shown a trend of increasing battery pack capacity and decreasing range extender (engine) power. Based on this trend, the number of cylinders in the engine can be reduced, thereby reducing costs. However, after reducing the number of engine cylinders, the balance law of the original crankshaft connecting rod and other moving parts changes, resulting in greater engine vibration and noise, and even damage. It is necessary to re-optimize the mechanical balance characteristics of the engine's crankshaft connecting rod mechanism. Summary of the Invention

[0004] To address at least one of the technical problems in the prior art, embodiments of this disclosure provide a V-type engine capable of reducing vibration of the V-type engine body.

[0005] Embodiments of this disclosure provide a V-type engine, comprising: a body; a crankshaft disposed on the body; two sets of drive assemblies, each set of drive assemblies including: a cylinder disposed above the body; a connecting rod, one end of which is connected to the crankshaft; a piston connected to the other end of the connecting rod; and a balancing assembly, wherein the crankshaft drives the balancing assembly to operate via a transmission mechanism, the balancing assembly being configured to provide a lateral force to the crankshaft via the transmission mechanism, suitable for counteracting at least a portion of the inertial force, in response to the inertial force generated in the cylinder by the alternating reciprocating motion of the two pistons and acting on the crankshaft, thereby reducing vibration of the body.

[0006] According to some embodiments of this disclosure, the aforementioned balancing assembly includes: a housing disposed in the aforementioned body; a camshaft disposed in the aforementioned housing parallel to the aforementioned crankshaft and configured to rotate under the drive of the aforementioned crankshaft via the aforementioned transmission mechanism; at least one cam mounted at intervals on the aforementioned camshaft, each of the aforementioned cams including a circular portion and two radially opposing protrusions extending radially outward from the aforementioned circular portion; and at least one set of elastic components mounted within the aforementioned housing and extending radially outward from the aforementioned cams, each set of the aforementioned elastic components being configured to be compressed upon contact with the aforementioned protrusions and to be reset upon contact with the aforementioned circular portion in response to the rotation of the aforementioned camshaft.

[0007] According to some embodiments of the present disclosure, at least one of the protrusions of the cam is located in the same radial direction, such that the protrusions located on the same side of the cam simultaneously compress at least one of the elastic components to contract.

[0008] According to some embodiments of this disclosure, when each of the pistons moves to the bottom dead center or the top dead center, a protrusion in each of the cams compresses the corresponding elastic component to contract, so that the elastic force generated by the elastic component is transmitted to the crankshaft through the camshaft and the transmission mechanism, and forms the lateral force.

[0009] According to some embodiments of this disclosure, the above-described balancing assembly includes two cams and two sets of elastic components.

[0010] According to some embodiments of the present disclosure, the camshaft includes two support bearings respectively disposed at both ends of the camshaft, and the two support bearings are configured to rotatably support the camshaft.

[0011] According to some embodiments of this disclosure, at least one through groove is provided parallel inside the housing to accommodate the elastic components respectively. The balancing component further includes a top cover disposed in the housing to confine the elastic components respectively within the through groove.

[0012] According to some embodiments of this disclosure, each set of the above-mentioned elastic components includes: an elastic member, one end of which abuts against the top cover; and a sliding member, sleeved on the other end of the elastic member, the other end of which abuts against the cam via the sliding member, the sliding member being configured to reciprocate within the through groove in response to periodic contact with the protrusion and the circular portion of the cam during the rotation of the camshaft.

[0013] According to some embodiments of this disclosure, the transmission mechanism includes a gear set meshing between the camshaft and the crankshaft, such that the camshaft rotates under the drive of the crankshaft.

[0014] According to some embodiments of this disclosure, the crankshaft includes: a main bearing; a crankshaft disposed on the main bearing, wherein the pistons of the two sets of the drive components are respectively connected to the crankshaft via two connecting rods; and two balance blocks mounted on the main bearing to balance the reciprocating inertial force of the connecting rods of the two sets of drive components and the rotational inertial force of the crankshaft.

[0015] According to an embodiment of the present disclosure, a V-type engine includes a body, a crankshaft, two sets of drive assemblies, and a balancing assembly. The crankshaft is disposed on the body. Each of the two sets of drive assemblies includes a cylinder, a connecting rod, and a piston. The cylinder is disposed above the body. One end of the connecting rod is connected to the crankshaft, and the piston is connected to the other end of the connecting rod. The crankshaft drives the balancing assembly to move through a transmission mechanism. The balancing assembly is configured to respond to the inertial force generated in the cylinder by the alternating reciprocating motion of the two pistons and acting on the crankshaft. Through the transmission mechanism, it provides the crankshaft with a lateral force suitable for counteracting at least a portion of the inertial force, thereby reducing the vibration of the body. Attached Figure Description

[0016] Figure 1 This is a perspective view of a V-type engine according to an illustrative embodiment of the present disclosure;

[0017] Figure 2 This is a perspective view of a driving component according to an illustrative embodiment of the present disclosure;

[0018] Figure 3 This is an exploded view of the components of a balance assembly in a V-type engine according to an illustrative embodiment of the present disclosure;

[0019] Figure 4 This is a first-view cross-sectional view of a balancing assembly according to an illustrative embodiment of the present disclosure;

[0020] Figure 5 This is a second-view cross-sectional view of a balancing assembly according to an illustrative embodiment of the present disclosure;

[0021] Figure 6 This is a perspective view of a cam and camshaft according to an illustrative embodiment of the present disclosure;

[0022] Figure 7 yes Figure 6 A magnified view of part A in the middle.

[0023] The meanings of the reference numerals in the attached figure are as follows:

[0024] 1. Organism;

[0025] 100. First through hole;

[0026] 10. Main bearing;

[0027] 11. Curved turn;

[0028] 12. Connecting rod;

[0029] 13. Piston;

[0030] 14. Balance weights;

[0031] 2. Shell;

[0032] 200. Through groove;

[0033] 210. Second through hole;

[0034] 3. Camshaft;

[0035] 31. Support bearing;

[0036] 4. Cam;

[0037] 41. Protrusion;

[0038] 5. Top cover;

[0039] 6. Elastic components;

[0040] 7. Sliding components;

[0041] 8. Fixing components;

[0042] 9. Second gear. Detailed Implementation

[0043] The embodiments of the present disclosure will now be described with reference to the accompanying drawings. However, it should be understood that these descriptions are exemplary only and are not intended to limit the scope of the disclosure. In the following detailed description, numerous specific details are set forth to provide a thorough understanding of the embodiments of the present disclosure for ease of explanation. However, it will be apparent that one or more embodiments may be practiced without these specific details. Furthermore, descriptions of well-known structures and techniques are omitted in the following description to avoid unnecessarily obscuring the concepts of the present disclosure.

[0044] The terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit this disclosure. The terms “comprising,” “including,” etc., as used herein indicate the presence of the stated features, steps, operations, and / or components, but do not exclude the presence or addition of one or more other features, steps, operations, or components.

[0045] All terms used herein (including technical and scientific terms) have the meanings commonly understood by those skilled in the art, unless otherwise defined. It should be noted that the terms used herein are to be interpreted in a manner consistent with the context of this specification, and not in an idealized or overly rigid way.

[0046] When using expressions such as "at least one of A, B, and C," the expression should generally be interpreted in accordance with the meaning commonly understood by a person skilled in the art (e.g., "a system having at least one of A, B, and C" should include, but is not limited to, systems having A alone, having B alone, having C alone, having A and B, having A and C, having B and C, and / or having A, B, and C, etc.). When using expressions such as "at least one of A, B, or C," the expression should generally be interpreted in accordance with the meaning commonly understood by a person skilled in the art (e.g., "a system having at least one of A, B, or C" should include, but is not limited to, systems having A alone, having B alone, having C alone, having A and B, having A and C, having B and C, and / or having A, B, and C, etc.).

[0047] Given the decreasing power of range extenders (engines), the number of cylinders in the engine can be reduced to lower costs. However, reducing the number of engine cylinders alters the balance of moving parts such as the crankshaft and connecting rods, leading to increased engine vibration and noise, and even damage. This necessitates re-optimizing the mechanical balance characteristics of the engine's crankshaft and connecting rod mechanism. Currently, the existing balancing structure primarily uses a balance shaft, driven by the engine crankshaft, to balance the rotational and reciprocating inertial forces generated during the crankshaft and connecting rod mechanism's movement. This structure is complex and costly, and is typically only used in high-end vehicles.

[0048] To address the problem of high vibration and noise during V-type engine operation, according to one aspect of the inventive concept of this disclosure, a V-type engine is provided. The V-type engine includes a body, a crankshaft, two sets of drive assemblies, and a balancing assembly. The crankshaft is disposed on the body. Each of the two sets of drive assemblies includes a cylinder, a connecting rod, and a piston. The cylinder is disposed above the body. One end of the connecting rod is connected to the crankshaft, and the piston is connected to the other end of the connecting rod. The crankshaft drives the balancing assembly to operate via a transmission mechanism. The balancing assembly is configured to respond to the inertial force generated in the cylinder by the alternating reciprocating motion of the two pistons and acting on the crankshaft. Through the transmission mechanism and the body, it provides the crankshaft with a lateral force suitable for counteracting at least a portion of the inertial force, thereby reducing the vibration of the body.

[0049] Figure 1 This is a perspective view of a V-type engine according to an illustrative embodiment of the present disclosure. Figure 2 This is a perspective view of a driving component according to an illustrative embodiment of the present disclosure.

[0050] A V-type engine is provided according to embodiments of this disclosure, such as Figure 1 and Figure 2As shown, the assembly includes a body 1, a crankshaft, two sets of drive components, and a balancing assembly. The crankshaft is mounted on the body 1. Each drive component includes a cylinder, a connecting rod 12, and a piston 13. The cylinder is positioned above the body 1. One end of the connecting rod 12 is connected to the crankshaft, and the piston 13 is connected to the other end of the connecting rod 12. The crankshaft drives the balancing assembly via a transmission mechanism. The balancing assembly is configured to respond to the inertial force generated within the cylinder by the alternating reciprocating motion of the two pistons 13 and acting on the crankshaft. Through the transmission mechanism, it provides the crankshaft with a lateral force suitable for counteracting at least a portion of the inertial force, thereby reducing the vibration of the body 1.

[0051] According to an embodiment of this disclosure, a first through hole 100 is provided on the body 1 along the X direction, and a crankshaft is disposed on the body 1 and passes through the first through hole 100.

[0052] According to embodiments of this disclosure, two pistons 13 utilize the gas pressure within their respective cylinders to drive a crankshaft via connecting rods 12. The crankshaft converts the alternating reciprocating motion of the connecting rods 12 into torque, which is output to perform work and drive the V-type engine. During the alternating reciprocating motion of the two pistons 13, a first-order reciprocating inertial force is generated within each of the two cylinders due to their linear reciprocating motion. When each piston 13 moves from top dead center to bottom dead center, or from bottom dead center to top dead center, a first-order reciprocating inertial force is generated due to the change in velocity. The magnitude of the first-order reciprocating inertial force is proportional to the mass and acceleration of the piston 13, and its direction is always along the direction of piston 13 movement.

[0053] According to embodiments of this disclosure, due to the interaction between the centrifugal force generated by the rotation of the crankshaft and the first-order reciprocating inertial force, the two pistons 13 generate lateral forces, i.e., second-order reciprocating inertial forces, in the two cylinders respectively. These lateral forces cause uneven wear on the cylinder walls. Because the movements of the two pistons 13 have a phase difference, the resultant force of the second-order reciprocating inertial forces generated by the two pistons 13 in the two cylinders is a second-order inertial force. The magnitude and direction of this second-order inertial force exhibit periodic changes, and its magnitude, direction, and the angle between the two cylinders are related. This second-order inertial force ultimately acts on the engine block 1 through the crankshaft, increasing vibration and noise within the V-type engine block 1. Therefore, for low-cylinder extended-range electric vehicles (REEVs), a balancing assembly is installed in the engine block 1, and the crankshaft drives the balancing assembly through a transmission mechanism. The balancing assembly is configured to respond to inertial forces (such as... Figure 1 The component of the force in the Y direction (as shown) provides a lateral force to the crankshaft through the transmission mechanism, which is suitable for counteracting at least a portion of the inertial force, so as to reduce the vibration of the body 1.

[0054] According to an embodiment of this disclosure, an inertial force acts on the crankshaft, and the resultant force of the inertial force R can be calculated using the following formula (1):

[0055] (1);

[0056] in, This indicates the angle between two cylinders. It indicates the angle the crankshaft has rotated since top dead center.

[0057] According to embodiments of this disclosure, first-order inertial force It can be calculated using the following formula (2):

[0058] (2);

[0059] According to embodiments of this disclosure, second-order inertial force It can be calculated using the following formula (3):

[0060] (3);

[0061] According to embodiments of this disclosure, C in formulas (1), (2), and (3) can be represented by the following formula (4):

[0062] (4);

[0063] in, The reciprocating mass is represented by the mass of piston 13 and the mass of the upper half of the center of mass of connecting rod 12, and r is represented by the radius of gyration of the crankshaft. This is expressed as rotational speed.

[0064] According to embodiments of this disclosure, in formulas (1) and (3) It can be expressed by the following formula (5):

[0065] (5);

[0066] Where L represents the length of link 12.

[0067] According to embodiments of this disclosure, the magnitude of the inertial force varies with the alternating reciprocating motion of the two pistons 13, such as... Figure 1 As shown, the alternation in the Y direction (the X, Y and Z directions are orthogonal to each other) occurs with the alternating reciprocating motion of the two pistons 13. The inertial force gradually decreases in the -Y direction and then gradually increases in the +Y direction (the +Y direction is the direction from the geometric center of the crankshaft section to the geometric center of the camshaft section), and repeats in a cycle.

[0068] According to embodiments of this disclosure, the included angle between the two cylinders can be 55°, 60°, and 90°, etc. It can be clearly seen from formula (1) that the inertial force R includes the first-order inertial force. and second-order inertial force Two parts. First-order inertial force It changes in a sinusoidal form, with the same period as the crankshaft motion. Second-order inertial force. It changes in a sinusoidal form, and its period of change is half the period of crankshaft motion.

[0069] According to embodiments of this disclosure, the elastic component (described in detail below) in the balancing assembly reciprocates under the action of a cam (described in detail below). The acceleration variation of the elastic component's motion follows a sinusoidal form, and the resulting lateral force can cancel out the inertial force R. By setting different cams, different elastic components can be controlled to reciprocate, generating a magnitude and a first-order inertial force. (Formula 2) and second-order inertial force The equal lateral forces in (Formula 3) cancel each other out, thus balancing the inertial force.

[0070] From formulas (1), (2), and (3), it is clear that when the included angle between the two cylinders... At that time, first-order inertial force Inertial force The inertial force R can be counteracted simply by constructing an elastic component that reciprocates under the action of a cam.

[0071] Figure 3 This is an exploded view of the components of a balance assembly in a V-type engine according to an illustrative embodiment of the present disclosure. Figure 4 This is a first-view cross-sectional view of a balancing assembly according to an illustrative embodiment of the present disclosure. Figure 5 This is a second-view cross-sectional view of a balancing assembly according to an illustrative embodiment of the present disclosure. Figure 6 This is a perspective view of a cam and camshaft according to an illustrative embodiment of the present disclosure. Figure 7 yes Figure 6 A magnified view of part A in the middle.

[0072] According to embodiments of this disclosure, such as Figure 3 , Figure 4 and Figure 5 As shown, the balancing assembly includes a housing 2, a camshaft 3, at least one cam 4, and at least one set of elastic components. The housing 2 is disposed within the body 1, and the camshaft 3 is disposed parallel to the crankshaft within the housing 2. The camshaft 3 is configured to rotate under the drive of the crankshaft via a transmission mechanism. Figure 6 and Figure 7As shown, at least one cam 4 is mounted on the camshaft 3 at intervals. Each cam 4 includes a circular portion and two radially opposing protrusions 41 that project radially outward from the circular portion. At least one set of elastic components is mounted within the housing 2 and extends radially outward from the cam 4 respectively. Each set of elastic components is configured to be compressed upon contact with the protrusions 41 in response to rotation of the camshaft 3 and to reset upon contact with the circular portion (each set of elastic components remains in contact with the cam 4 throughout rotation).

[0073] According to an embodiment of this disclosure, a second through hole 210 is provided on the housing 2 along the X direction, and the camshaft 3 is disposed on the housing 2 and passes through the second through hole 210.

[0074] According to embodiments of the present disclosure, each set of elastic components is configured to respond to the rotation of the camshaft 3, which rotates at the same speed as the crankshaft, and is compressed when in contact with the protrusion 41 of each cam 4. The elastic force generated by each set of elastic components is transmitted to the crankshaft through the camshaft 3 and the transmission mechanism, and forms a lateral force (reaction force). The lateral force (reaction force) formed can counteract at least a portion of the inertial force to reduce the vibration of the body 1.

[0075] According to an embodiment of the present disclosure, at least one cam 4 has a protrusion 41 located in the same radial direction, such that the protrusions 41 located on the same side of the cam 4 simultaneously compress at least one elastic component to contract.

[0076] According to embodiments of this disclosure, the number of cams 4 and elastic components included in the balancing assembly can be one, two, three, etc.

[0077] According to an embodiment of this disclosure, taking a balancing assembly comprising two cams 4 and two sets of elastic components as an example, the two cams 4 are mounted on the camshaft 3 at intervals, and the two sets of elastic components are mounted in the housing 2 and arranged side by side at intervals along the axial direction of the camshaft 3. The protrusions 41 of the two cams 4 are located in the same radial direction, such that the protrusions 41 located on the same side of the two cams 4 simultaneously squeeze the two sets of elastic components to contract. The two sets of elastic components reciprocate under the drive of the two cams 4. The profile of the cams 4 determines that their motion process is an acceleration change that satisfies a sine form. The lateral force generated during their motion process can offset all or at least part of the second-order inertial force, thereby reducing the vibration of the engine body 1 caused by the inertial force and achieving the balance of the V-type engine.

[0078] According to embodiments of this disclosure, when each piston 13 moves to the bottom dead center or the top dead center, a protrusion 41 in each cam 4 compresses the corresponding elastic component to contract, so that the elastic force generated by the elastic component is transmitted to the crankshaft through the camshaft 3 and the transmission mechanism, and forms a lateral force.

[0079] According to embodiments of this disclosure, when each piston 13 moves to bottom dead center, a protrusion 41 in each cam 4 compresses the corresponding elastic component to contract once, causing a change in the force on each cam 4. The elastic force generated by the elastic component is transmitted to the crankshaft through the camshaft 3 and the transmission mechanism, forming a lateral force (reaction force) to buffer the rotational vibration of the crankshaft. When each piston 13 moves to top dead center, another protrusion 41 in each cam 4, radially opposite to one protrusion 41, compresses the corresponding elastic component to contract again (the two contractions of the protrusion 41 compressing the corresponding elastic component are a continuous process), causing a change in the force on each cam 4 again. The elastic force generated by the elastic component is transmitted to the crankshaft through the camshaft 3 and the transmission mechanism, again forming a lateral force (reaction force) to counteract at least a portion of the inertial force, thereby reducing the vibration of the machine body 1.

[0080] According to embodiments of this disclosure, such as Figure 6 As shown, the camshaft 3 includes two support bearings 31, which are respectively disposed at both ends of the camshaft 3. The two support bearings 31 are configured to rotatably support the camshaft 3.

[0081] According to embodiments of this disclosure, two support bearings 31 are respectively provided at both ends of the camshaft 3, which can reduce the friction between the camshaft 3 and the housing 2, thereby reducing wear and extending the service life of the camshaft 3. Furthermore, the support bearings 31 at both ends of the camshaft 3 can reduce the vibration of the camshaft 3 during high-speed operation, thereby reducing noise caused by vibration. The two support bearings 31 rotatably support the camshaft 3, allowing the two support bearings 31 to be positioned or adjusted relative to the camshaft 3, facilitating subsequent maintenance and replacement of the camshaft 3. Simultaneously, the two support bearings 31 can effectively bear the weight of the camshaft 3 and the forces generated during rotation, and evenly distribute these loads onto the housing 2, thereby improving the smoothness, stability, and reliability of the V-type engine's operation.

[0082] According to embodiments of this disclosure, such as Figure 3 As shown, at least one through groove 200 is provided parallel inside the housing 2 to accommodate the elastic components respectively. The balancing component also includes a top cover 5, which is disposed in the housing 2 to confine the elastic components within the through groove 200 respectively.

[0083] According to an embodiment of this disclosure, the top cover 5 confines at least one set of elastic components within the through groove 200, thereby preventing the elastic components from disengaging from the through groove 200 when compressed and contracted by the cam 4.

[0084] According to an embodiment of this disclosure, the top cover 5 is connected to the housing 2 by a plurality of fixing components 8, the fixing components 8 including bolts and flat washers, and the top cover 5 is fixed to the housing 2 by threaded connection.

[0085] According to an embodiment of the present disclosure, when the balancing assembly includes two cams 4 and two sets of elastic components, two through slots 200 are provided parallel to each other in the housing 2 and extend radially outward from the two cams 4 respectively to accommodate the two sets of elastic components.

[0086] According to embodiments of this disclosure, such as Figure 3 As shown, each set of elastic components includes an elastic element 6 and a sliding element 7. One end of the elastic element 6 abuts against the top cover 5, and the sliding element 7 is sleeved on the other end of the elastic element 6. The other end of the elastic element 6 abuts against the cam 4 through the sliding element 7. The sliding element 7 is configured to reciprocate within the through groove 200 in response to periodic contact with the protrusion 41 and the round portion of the cam 4 during the rotation of the camshaft 3.

[0087] In one illustrative embodiment, the slider 7 is constructed as a hollow cylinder with an opening on one side. The opening side of the slider 7 is fitted onto the other end of the elastic member 6, and a positioning hole is provided on the other side opposite to the opening side. Figure 3 (Not shown in the image) The other end of the elastic element 6 is connected to the positioning hole to prevent the elastic element 6 from disengaging from the sliding element 7 during the compression and reset process in the through groove 200 in response to the reciprocating sliding of the sliding element 7, thereby enhancing the structural compactness of the elastic component.

[0088] According to embodiments of this disclosure, the lateral force is determined based on the speed ratio of the first gear and the second gear 9 in the transmission mechanism (the first gear and the second gear 9 are described in detail below), the profile of each cam 4, the stiffness of the elastic element 6, and the mass of the sliding element 7. The magnitude of the required balancing force is determined by the unbalanced inertial force of the V-type engine.

[0089] According to an embodiment of the present disclosure, the transmission mechanism includes a gear set meshing between the camshaft 3 and the crankshaft, causing the camshaft 3 to rotate under the drive of the crankshaft.

[0090] According to an embodiment of this disclosure, the gear set includes a first gear and a second gear 9, the first gear being disposed at one end of the crankshaft ( Figure 1 (not shown in the image), such as Figure 1 As shown, the second gear 9 is located at one end of the camshaft 3, and the first gear and the second gear 9 mesh with each other, so that the camshaft 3 can rotate under the drive of the crankshaft.

[0091] According to embodiments of this disclosure, the transmission mechanism may also be selected as a toothed belt transmission.

[0092] According to embodiments of this disclosure, such as Figure 2As shown, the crankshaft includes a main bearing 10, a crank 11, and two balance blocks 14. The crank 11 is mounted on the main bearing 10. The pistons 13 of the two drive components are connected to the crank 11 via two connecting rods 12. The two balance blocks 14 are mounted on the main bearing 10 to balance the reciprocating inertial force of the connecting rods 12 of the two drive components and the rotational inertial force of the crankshaft.

[0093] According to embodiments of this disclosure, when the included angle between the connecting rods of the two cylinders is 90°, by installing a balance block 14 on the main bearing 10 to balance the partial reciprocating inertial force of the connecting rods 12 of the two sets of drive components reciprocating, namely the first-order reciprocating inertial force, and to balance the rotational inertial force of the crankshaft, the overall vibration of the V-type engine can be reduced, and the vibration noise can be reduced.

[0094] Those skilled in the art will understand that the features described in the various embodiments and / or claims of this disclosure can be combined or combined in various ways, even if such combinations or combinations are not explicitly described in this disclosure. In particular, the features described in the various embodiments and / or claims of this disclosure can be combined and / or combined in various ways without departing from the spirit and teachings of this disclosure. All such combinations and / or combinations fall within the scope of this disclosure.

[0095] It should also be noted that the directional terms mentioned in the embodiments, such as "up," "down," "front," "back," "left," and "right," are only for reference to the directions in the accompanying drawings and are not intended to limit the scope of protection of this disclosure. Throughout the drawings, the same elements are represented by the same or similar reference numerals. Conventional structures or constructions will be omitted where they may cause confusion in understanding this disclosure, and the shapes and dimensions of the components in the drawings do not reflect actual size and proportion, but are only schematic representations of the embodiments of this disclosure.

[0096] Unless otherwise stated, the numerical parameters in this specification and the appended claims are approximate values ​​and can be varied according to desired characteristics derived from the content of this disclosure. Specifically, all figures used in the specification and claims to indicate composition, reaction conditions, etc., should be understood to be modified by the term "about" in all cases. Generally, this means that a specific amount may vary by ±10% in some embodiments, ±5% in some embodiments, ±1% in some embodiments, and ±0.5% in some embodiments.

[0097] The use of ordinal numbers such as "first," "second," "third," etc., in the specification and claims to modify the corresponding elements does not imply that the element has any ordinal number, nor does it represent the order of one element with another element, or the order of manufacturing methods. The use of these ordinal numbers is only to enable a named element to be clearly distinguished from another element with the same name.

[0098] Furthermore, unless specifically described or required to occur in a specific order, the order of the above steps is not limited to those listed above and can be varied or rearranged according to the desired design. Moreover, the above embodiments can be used in combination with each other or with other embodiments based on design and reliability considerations; that is, technical features from different embodiments can be freely combined to form more embodiments.

[0099] The embodiments of this disclosure have been described above. However, these embodiments are for illustrative purposes only and are not intended to limit the scope of this disclosure. Although various embodiments have been described above, this does not mean that the measures in the various embodiments cannot be used advantageously in combination. The scope of this disclosure is defined by the appended claims and their equivalents. Various substitutions and modifications can be made by those skilled in the art without departing from the scope of this disclosure, and all such substitutions and modifications should fall within the scope of this disclosure.

Claims

1. A V-type engine, characterized in that, include: Organism; The crankshaft is disposed in the machine body; Two sets of drive components, each set of drive components including: A cylinder is located above the machine body; A connecting rod, one end of which is connected to the crankshaft; A piston, which is connected to the other end of the connecting rod; A balancing assembly, driven by a transmission mechanism, is configured to provide a lateral force to the crankshaft via the transmission mechanism to counteract at least a portion of the inertial force generated within the cylinder by the alternating reciprocating motion of the two pistons and acting on the crankshaft, thereby reducing vibration of the machine body.

2. The V-type engine according to claim 1, characterized in that, The balancing component includes: A housing, disposed on the body; A camshaft, disposed parallel to the crankshaft in the housing, is configured to rotate under the drive of the crankshaft via the transmission mechanism; At least one cam is mounted at intervals on the camshaft, each cam including a circular portion and two protrusions that project radially outward from the circular portion and are radially opposite to each other; At least one set of elastic components is installed within the housing and extends radially outward from the cam, each set of elastic components being configured to be compressed upon contact with the protrusion and to be reset upon contact with the circular portion in response to rotation of the camshaft.

3. The V-type engine according to claim 2, characterized in that, At least one of the cam's protrusions is located in the same radial direction, such that the protrusions located on the same side of the cam simultaneously compress at least one of the elastic components to contract.

4. The V-type engine according to claim 3, characterized in that, When each piston moves to the bottom dead center or top dead center, a protrusion in each cam compresses the corresponding elastic component to contract, so that the elastic force generated by the elastic component is transmitted to the crankshaft through the camshaft and transmission mechanism, and forms the lateral force.

5. The V-type engine according to claim 2, characterized in that, The balancing assembly includes two cams and two sets of elastic components.

6. The V-type engine according to claim 2, characterized in that, The camshaft includes: Two support bearings are respectively disposed at both ends of the camshaft, and the two support bearings are configured to rotatably support the camshaft.

7. The V-type engine according to claim 2, characterized in that, At least one through slot is provided parallel to each other within the housing to accommodate the elastic components, and the balancing component further includes: A top cover is disposed on the housing to confine the resilient components within the through slots.

8. The V-type engine according to claim 7, characterized in that, Each set of resilient components includes: An elastic element, one end of which abuts against the top cover; A slider is sleeved on the other end of the elastic member, the other end of the elastic member abutting against the cam via the slider. The slider is configured to reciprocate within the through groove in response to periodic contact with the protrusions and circular portions of the cam during rotation of the camshaft.

9. The V-type engine according to claim 2, characterized in that, The transmission mechanism includes: A gear set meshes between the camshaft and the crankshaft, causing the camshaft to rotate under the drive of the crankshaft.

10. The V-type engine according to claim 1, characterized in that, The crankshaft includes: Main bearing; A crank is mounted on the main bearing, and the pistons of the two sets of drive components are respectively connected to the crank via two connecting rods; Two counterweights are mounted on the main bearing to balance the reciprocating inertial force of the connecting rods of the two sets of drive components and the rotational inertial force of the crankshaft.

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