Balance shaft assembly, engine, power assembly and vehicle

Abstract

The utility model discloses a balance shaft assembly, engine, power assembly and vehicle, balance shaft assembly includes: first gear, the first gear includes: main tooth gear, vice tooth gear and arc elastic piece, main tooth gear and vice tooth gear are arranged in the front-back direction, arc elastic piece is arranged around the axis of first gear, and the first gear is connected with the vice tooth gear. The first end and the second end are arranged in a spaced mode in the axis direction of the first gear, the first end is connected with the main tooth gear, and the second end is connected with the auxiliary tooth gear. Therefore, the meshing back clearance between the first gear and the second gear can be more effectively and reliably eliminated, knocking noise generated by meshing of the first gear and the second gear is reduced, the NVH performance of the balance shaft assembly is improved, radial acting force can be avoided, and the balance performance of the balance shaft assembly is improved.

Description

Technical Field

[0001] The utility model relates to the technical field of vehicles, in particular to a balance shaft assembly, an engine, a power assembly and a vehicle. Background Art

[0002] In order to ensure the balance of the engine and reduce the vibration of the engine, a balance shaft assembly is often installed in the engine. The balance shaft rotates at a high speed, and the bearings, gears and other moving parts in the balance shaft assembly will generate noise under high-speed rotation, affecting the NVH performance of the balance shaft assembly.

[0003] In the related art, the structure of the balance shaft assembly and the arrangement of its components are not reasonable enough, resulting in high noise and vibration during operation of the balance shaft assembly, affecting the comfort experience of passengers in the cab. Some balance shaft assemblies use scissor teeth to reduce the knocking noise generated by gear meshing, but the structural design of the scissor teeth is not reasonable enough, not only the knocking noise reduction effect on the gear meshing is poor, but also the structure is relatively complicated. Utility Model Content

[0004] The utility model aims to solve at least one of the technical problems existing in the prior art. To this end, one purpose of the utility model is to provide a balance shaft assembly, which has better NVH performance.

[0005] The utility model further provides an engine.

[0006] The utility model further provides a power assembly.

[0007] The utility model further provides a vehicle.

[0008] According to an embodiment of the utility model, the balance shaft assembly includes: a first gear, the first gear includes: a main gear, a secondary gear and an arc-shaped elastic member, the main gear and the secondary gear are arranged in the front-to-back direction, the arc-shaped elastic member is arranged around the axis of the first gear, and has a first end and a second end spaced apart around the axis direction of the first gear, the first end is connected to the main gear, and the second end is connected to the secondary gear.

[0009] Therefore, by arranging the arc-shaped elastic member around the axis of the first gear and having a first end and a second end arranged at intervals around the axis of the first gear, the first end is connected to the main gear and the second end is connected to the auxiliary gear. This can not only more effectively and reliably eliminate the meshing backlash between the first gear and the second gear, reduce the knocking noise generated by the meshing of the first gear and the second gear, and improve the NVH performance of the balance shaft assembly, but also avoid the generation of radial force and improve the balancing performance of the balance shaft assembly.

[0010] In some examples of the present invention, the central angle of the arc-shaped elastic member is α, and α satisfies the relationship: α≥270°.

[0011] In some examples of the present invention, the first gear further includes: a first locating pin and a second locating pin, wherein both ends of the first locating pin are respectively connected to the main tooth gear and the first end, and both ends of the second locating pin are respectively connected to the auxiliary tooth gear and the second end.

[0012] In some examples of the utility model, a first positioning pin hole is provided on the main tooth gear, a second positioning pin hole is provided on the auxiliary tooth gear, a third positioning pin hole is opened at the first end, and a fourth positioning pin hole is opened at the second end, one end of the first positioning pin is interference fit with the first positioning pin hole and the other end is penetrated by the third positioning pin hole, one end of the second positioning pin is interference fit with the second positioning pin hole and the other end is penetrated by the fourth positioning pin hole.

[0013] In some examples of the present invention, the first gear further includes: an axial force applying member, which is disposed on a side of the auxiliary gear away from the main gear and abuts against the auxiliary gear.

[0014] In some examples of the present invention, the axial force applying member is a disc spring.

[0015] In some examples of the present utility model, a first weight-reducing hole is provided on the disc spring, and there are a plurality of the first weight-reducing holes, which are spaced apart in the circumferential direction of the disc spring.

[0016] In some examples of the present invention, the first gear also includes: a first clamping ring, a first boss is provided on the main tooth gear, the first boss is coaxial with the main tooth gear and extends toward the auxiliary tooth gear, a first mounting groove is provided on the first boss, a circular hole is provided on the auxiliary tooth gear, the circular hole is coaxial with the auxiliary tooth gear, the first boss is sequentially penetrated by the arc-shaped elastic member, the circular hole, the axial force member and the first clamping ring, the first clamping ring is provided in the first mounting groove, and the first clamping ring abuts against the side of the axial force member away from the auxiliary tooth gear.

[0017] In some examples of the present invention, a second boss is also provided on the auxiliary tooth gear, the diameter of the second boss is larger than the diameter of the first boss, the second boss is coaxial with the auxiliary tooth gear and extends toward the main tooth gear, and a groove is provided on the main tooth gear, the diameter of the groove is the same as the diameter of the second boss, and the second boss extends into the groove and is loosely matched with the groove.

[0018] In some examples of the present invention, the balance shaft assembly also includes a second gear, which is respectively meshed with the main gear and the auxiliary gear, and a plurality of second weight reduction holes are provided on the second gear. The number of the second weight reduction holes is multiple, and the plurality of second weight reduction holes are spaced apart in the circumferential direction of the second gear.

[0019] In some examples of the present invention, the balance shaft assembly also includes a second gear, which is respectively meshed with the main gear and the auxiliary gear, and the center of gravity of the second gear falls on the rotation axis of the second gear, and the center of gravity of the first gear falls on the rotation axis of the first gear.

[0020] In some examples of the present utility model, the balancing shaft assembly further includes: a second gear, a housing, an active balancing shaft assembly and a driven balancing shaft assembly, the second gear is respectively meshed with the main gear and the auxiliary gear, the active balancing shaft assembly is rotatably disposed in the housing and includes: an active balancing shaft, a first active bearing and the second gear, the second gear is disposed on the active balancing shaft, the first active bearing is disposed at one end of the active balancing shaft close to the second gear and located in front of the second gear, an active stop step is disposed on the housing, the active stop step is located behind the first active bearing and is limitedly matched with the first active bearing; the driven balancing shaft assembly is rotatably disposed in the housing and includes: a driven balancing shaft, a first driven bearing and the first gear, the first gear is disposed on the driven balancing shaft, the first driven bearing is disposed at one end of the driven balancing shaft close to the first gear and located in front of the first gear, a driven stop step is disposed on the housing, the driven stop step is located behind the first driven bearing and is limitedly matched with the first driven bearing.

[0021] In some examples of the present utility model, the active balancing shaft assembly also includes: a second active bearing and a second clamping ring, the second active bearing is arranged at the end of the active balancing shaft away from the second gear, the housing is provided with a second mounting groove, the second clamping ring is arranged in the second mounting groove and is located in front of the second active bearing, and the second clamping ring is limitedly matched with the second active bearing; the driven balancing shaft assembly also includes: a second driven bearing and a third clamping ring, the second driven bearing is arranged at the end of the driven balancing shaft away from the first gear, the housing is provided with a third mounting groove, the third clamping ring is arranged in the third mounting groove and is located in front of the second driven bearing, and the third clamping ring is limitedly matched with the second driven bearing.

[0022] In some examples of the present invention, the first active bearing, the second active bearing, the first driven bearing, and the second driven bearing are all deep groove ball bearings.

[0023] In some examples of the present invention, an active balancing block is provided on the active balancing shaft, the active balancing block is located between the first active bearing and the second active bearing, the active balancing block is semi-cylindrical, and the axis of the active balancing block is collinear with the axis of the active balancing shaft; a driven balancing block is provided on the driven balancing shaft, the driven balancing block is located between the first driven bearing and the second driven bearing, the driven balancing block is semi-cylindrical, and the axis of the driven balancing block is collinear with the axis of the driven balancing shaft.

[0024] In some examples of the present invention, the active balancing block and the active balancing shaft are integrally formed spheroidal cast iron structures, and the driven balancing block and the driven balancing shaft are integrally formed spheroidal cast iron structures.

[0025] In some examples of the present invention, an active reinforcing rib is provided on the active balancing shaft, the active reinforcing rib is located on a side of the active balancing shaft away from the active balancing block, the active reinforcing rib is extended in the axial direction of the active balancing shaft and has the same length as the active balancing block; a driven reinforcing rib is provided on the driven balancing shaft, the driven reinforcing rib is located on a side of the driven balancing shaft away from the driven balancing block, the driven reinforcing rib is extended in the axial direction of the driven balancing shaft and has the same length as the driven balancing block.

[0026] In some examples of the present utility model, the shell includes an upper shell, a lower shell and a first fastener, the upper shell and the lower shell are arranged relative to each other, a plurality of first perforations are arranged on the upper shell, and a plurality of second perforations are arranged on the lower shell, the plurality of first perforations and the plurality of second perforations correspond one to one, the first fastener simultaneously penetrates the first perforations and the second perforations to connect and fix the upper shell and the lower shell, and the upper shell and the lower shell are respectively integrally made structural parts.

[0027] In some examples of the utility model, a fifth positioning pin hole is provided on the upper shell, and there are two of the fifth positioning pin holes that are diagonally distributed on the upper shell. A sixth positioning pin hole is provided on the lower shell, and there are two of the sixth positioning pin holes that correspond one-to-one to the two fifth positioning pin holes. The shell also includes: a third positioning pin that is positioned and matched with the fifth positioning pin hole and the sixth positioning pin hole at the same time.

[0028] In some examples of the utility model, a locking pin hole is arranged at the bottom of the lower shell body, the active balancing shaft assembly includes an active balancing block, the driven balancing shaft assembly includes a driven balancing block, a phase positioning hole is arranged on the active balancing block and / or the driven balancing block, and the shell body also includes: a locking pin, and the locking pin selectively passes through the locking pin hole and the phase positioning hole at the same time.

[0029] The engine according to the embodiment of the utility model comprises: the balance shaft assembly described above.

[0030] In some embodiments of the utility model, the engine also includes: a cylinder body, in which a plurality of cylinders are arranged at intervals in the front-to-back direction, the symmetry plane of the plurality of cylinders in the left-to-right direction is a first plane, a crankshaft is arranged in the cylinder body, the crankshaft is provided with a crankshaft ring gear, and the balance shaft assembly is transmission-connected to the crankshaft ring gear; an oil pan, the oil pan is arranged on the lower surface of the cylinder body, the balance shaft assembly is arranged in the oil pan and includes: an active balance shaft assembly and a driven balance shaft assembly, the center of gravity of the active balance shaft assembly and the center of gravity of the driven balance shaft assembly being symmetrical about the first plane.

[0031] In some embodiments of the utility model, there are four cylinders and they are the first cylinder, the second cylinder, the third cylinder and the fourth cylinder in the front-to-back direction, the symmetry plane of the second cylinder and the third cylinder in the front-to-back direction is the second plane, the active balancing shaft assembly includes an active balancing block, the driven balancing shaft assembly includes a driven balancing block, and the center of gravity of the active balancing block and the center of gravity of the driven balancing block are both located on the second plane.

[0032] The power assembly according to the embodiment of the utility model includes: the engine described above.

[0033] A vehicle according to an embodiment of the utility model includes: the above-mentioned engine or the above-mentioned power assembly.

[0034] Additional aspects and advantages of the present invention will be given in part in the following description, and in part will become apparent from the following description, or will be learned through the practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0035] The above and / or additional aspects and advantages of the present invention will become apparent and easily understood from the description of the embodiments in conjunction with the following drawings, in which:

[0036] Figure 1 is an exploded view of an engine according to an embodiment of the utility model;

[0037] Figure 2is a schematic diagram of a balance shaft assembly according to an embodiment of the utility model;

[0038] Figure 3 is an exploded view of a balance shaft assembly according to an embodiment of the utility model;

[0039] Figure 4 is a partial schematic diagram of a balance shaft assembly according to an embodiment of the utility model;

[0040] Figure 5 is an exploded view of an active balancing shaft assembly according to an embodiment of the utility model;

[0041] Figure 6 is an exploded view of a driven balance shaft assembly according to an embodiment of the utility model;

[0042] Figure 7 is an exploded view of a first gear according to an embodiment of the utility model;

[0043] Figure 8 is an exploded view of the first gear from another perspective according to an embodiment of the utility model;

[0044] Fig. 9 is a schematic diagram of a housing according to an embodiment of the utility model;

[0045] Fig.10 is a cross-sectional view of a housing along the AA direction according to an embodiment of the utility model;

[0046] Fig.11 It is a cross-sectional view of the shell along the BB direction according to an embodiment of the utility model.

[0047] Reference numerals:

[0048] 1000, engine;

[0049] 100. Balance shaft assembly;

[0050] 10. Shell;

[0051] 11. upper shell; 111. first through hole; 112. fifth positioning pin hole; 113. third through hole; 114. waist-shaped hole;

[0052] 12. lower housing; 121. second through hole; 122. sixth positioning pin hole; 123. locking pin hole;

[0053] 13. first fastener; 14. third positioning pin; 15. locking pin; 16. active thrust step; 17. passive thrust step; 18. second mounting groove; 19. third mounting groove;

[0054] 20. Active balancing shaft assembly; 21. Active balancing shaft; 22. Active balancing block; 221. Phase positioning hole; 23. Second gear; 231. Second weight reduction hole; 24. First active bearing; 25. Second active bearing; 26. Second clamping ring; 27. Active reinforcing rib;

[0055] 30. driven balancing shaft assembly; 31. driven balancing shaft; 32. driven balancing block;

[0056] 33, first gear; 331, main gear; 3311, first positioning pin hole; 3312, first boss; 3313, first mounting groove; 3314, groove; 332, auxiliary gear; 3321, second positioning pin hole; 3322, second boss; 3323, round hole; 333, arc elastic member; 3331, third positioning pin hole; 3332, fourth positioning pin hole; 3333, first end; 3334, second end; 334, axial force member; 3341, first weight reduction hole; 335, first positioning pin; 336, second positioning pin; 337, first clamping ring;

[0057] 34. First driven bearing; 35. Second driven bearing; 36. Third clamping ring; 37. Driven reinforcing rib;

[0058] 40. A second fastener;

[0059] 200, cylinder body; 201, first cylinder; 202, second cylinder; 203, third cylinder; 204, fourth cylinder;

[0060] 300, crankshaft; 301, crankshaft gear ring;

[0061] 400. Oil pan. DETAILED DESCRIPTION

[0062] The embodiments of the present utility model are described in detail below. The embodiments described with reference to the accompanying drawings are exemplary. The embodiments of the present utility model are described in detail below.

[0063] Reference below Figure 1-Figure 11 A balancing shaft assembly 100 according to an embodiment of the present invention is described. The balancing shaft assembly 100 can be applied to an engine 1000 , the engine 1000 can be applied to a powertrain, and both the engine 1000 and the powertrain can be applied to a vehicle.

[0064] Combination Figure 3-Figure 8As shown, according to the utility model, the balance shaft assembly 100 can mainly include: a second gear 23 and a first gear 33, the first gear 33 is a scissor tooth, and the first gear 33 can mainly include: a main gear 331, a secondary gear 332 and an arc-shaped elastic member 333, the main gear 331 and the secondary gear 332 are arranged in the front-to-back direction and are both meshed with the second gear 23, the arc-shaped elastic member 333 is arranged around the axis of the first gear 33, and has a first end 3333 and a second end 3334 arranged at intervals around the axis direction of the first gear 33, the first end 3333 is connected to the main gear 331, and the second end 3334 is connected to the secondary gear 332.

[0065] Among them, the first gear 33 can be used as a gear for power input in the balance shaft assembly 100, that is, a driving gear, and can also be used as a gear for passive rotation in the balance shaft assembly, that is, a driven gear. In the embodiment of the utility model, the first gear 33 is described as a gear for passive rotation in the balance shaft assembly 100, that is, a driven gear. It should be noted that those skilled in the art can also use it as a gear for power input in the balance shaft assembly 100 according to the specification of this application.

[0066] Specifically, an active balancing shaft assembly 20 and a driven balancing shaft assembly 30 are provided in the balancing shaft assembly 100. The active balancing shaft assembly 20 is provided with a second gear 23, and the driven balancing shaft assembly 30 is provided with a first gear 33. By meshing the second gear 23 with the first gear 33, the second gear 23 can not only drive the active balancing shaft assembly 20 to rotate, but also drive the first gear 33 to rotate, thereby driving the driven balancing shaft assembly 30 to rotate, that is, through the mutual meshing of the second gear 23 and the first gear 33, the normal transmission of power in the balancing shaft assembly 100 can be guaranteed, and the normal operation of the balancing shaft assembly 100 can be guaranteed.

[0067] Taking into account the high rotation speed of the balance shaft assembly 100, which can even reach 11000r / min, it is necessary not only to strictly control the assembly and manufacturing accuracy of each sub-part of the balance shaft assembly 100, but also to strictly control the meshing transmission accuracy of the second gear 2332 and the first gear 3342, so as to ensure that the balance shaft assembly 100 has low noise and vibration when running in the engine 1000, and meet the comfort experience requirements of passengers in the cab.

[0068] By setting the second gear 23 as a smooth plate tooth, setting the first gear 33 as a scissor tooth, and arranging the main tooth gear 331 and the auxiliary tooth gear 332 in the front-to-back direction, connecting the first end 3333 of the arc-shaped elastic member 333 to the main tooth gear 331, and connecting the second end 3334 of the arc-shaped elastic member 333 to the auxiliary tooth gear 332, when the first gear 33 is meshed with the second gear 23, the C-shaped spring can be pulled apart by a certain distance, so that the C-shaped spring has an effect of acting between the main tooth gear 331 and the auxiliary tooth gear 332. The arc-shaped elastic member 333 can be used as a torsion limiter, so that the main gear 331 and the auxiliary gear 332 have a spring preload in two directions, so that the main gear 331 and the auxiliary gear 332 can be staggered at a certain angle relative to each other under the premise that the main gear 331 and the auxiliary gear 332 are meshed with the main gear 331 at the same time, thereby compensating for the gap formed after the gears are worn, that is, eliminating the meshing backlash between the first gear 33 and the second gear 23, and reducing the knocking noise generated by the meshing of the first gear 33 and the second gear 23.

[0069] Specifically, if Figure 2 As shown, the second gear 23 is arranged on the left side of the first gear 33. Taking the counterclockwise rotation of the second gear 23 and the clockwise rotation of the first gear 33 as an example, the lower side of the right side tooth of the second gear 23 is the active surface, and the upper side of the right side tooth of the second gear 23 is the driven surface. The left side tooth of the main gear 331 is in contact with the active surface. At the same time, under the action of the arc-shaped elastic member 333, the left side tooth of the auxiliary gear 332 is pressed against the driven surface of the second gear 23. Finally, when the first gear 33 and the second gear 23 are meshed, the main gear 331 and the auxiliary gear 332 are always in contact with the active surface and the driven surface of the second gear 23, thereby eliminating the gear meshing clearance and the gear knocking sound generated during the gear meshing process, reducing the vibration generated during the gear transmission process, and improving the NVH performance of the balance shaft assembly 100.

[0070] Compared with the linear elastic member, the arc-shaped elastic member 333 in this solution is arranged around the axis of the first gear 33, and the first end 3333 and the second end 3334 are arranged at intervals in the direction of the axis of the first gear 33, so that the direction of the elastic force applied by the arc-shaped elastic member 333 can be basically consistent with the tangent direction of the main gear 331 and the auxiliary gear 332, and the elastic force can more effectively drive the main gear 331 and the auxiliary gear 332 to stagger by a certain angle, and the elastic force in this direction is not easy to make the main gear 331 and the auxiliary gear 332 have a relative movement tendency in the radial direction, so that the main gear 331 and the auxiliary gear 332 are not easy to generate radial force on the driven balance shaft 31 installed on the first gear 33, and the balancing performance of the driven balance shaft 31 is guaranteed. It should be noted that the arc-shaped elastic member 333 can include but is not limited to a C-type spring.

[0071] In a specific embodiment of the present invention, the material of the second gear 23 can be 20MnCrS5, the second gear 23 is a helical gear, the helix angle is 28.8° (right-handed), the module is 1.3mm, the pressure angle is 15°, and the number of teeth is 59. Also, the material of the main gear 331 and the auxiliary gear 332 can both be 20MnCrS5, the main gear 331 and the auxiliary gear 332 are both helical gears, the helix angle is 28.8° (left-handed), the module is 1.3mm, the pressure angle is 15°, and the number of teeth is 59. In this way, the smooth transmission between the second gear 23 and the first gear 33 can be facilitated, and the NVH performance of the balance shaft assembly 100 can be improved.

[0072] Thus, by making the arc-shaped elastic member 333 be arranged around the axis of the first gear 33, and having a first end 3333 and a second end 3334 arranged at intervals around the axis direction of the first gear 33, the first end 3333 is connected to the main gear 331, and the second end 3334 is connected to the auxiliary gear 332, so that not only can the meshing backlash between the first gear 33 and the second gear 23 be eliminated more effectively and reliably, the knocking noise generated by the meshing of the first gear 33 and the second gear 23 be reduced, and the NVH performance of the balancing shaft assembly 100 be improved, but also the radial force on the driven balancing shaft 31 can be avoided, and the balancing performance of the balancing shaft assembly 100 can be improved. It should be noted that the center of the arc-shaped elastic member 333 may fall on the axis of the first gear 33, or may not fall on the axis of the first gear 33. When the center of the arc-shaped elastic member 333 falls on the axis of the first gear 33, the balancing performance is better.

[0073] Furthermore, the center angle of the arc-shaped elastic member 333 is α, and α satisfies the relationship: α≥270°. Specifically, by setting the center angle of the arc-shaped elastic member 333 to be not less than 270°, the structural design of the arc-shaped elastic member 333 can be optimized. After the first end 3333 is connected to the main gear 331 and the second end 3334 is connected to the auxiliary gear 332, the preload force of the arc-shaped elastic member 333 can be increased, so that the meshing clearance between the second gear 23 and the first gear 33 can be further better compensated, and the knocking noise generated by the meshing of the first gear 33 and the second gear 23 can be further reduced.

[0074] It should be noted that, in some other embodiments of the utility model, the central angle of the arc-shaped elastic member 333 can also be made 360 ​​degrees, so that the first end 3333 and the second end 3334 of the arc-shaped elastic member 333 are spaced apart in the axial direction, so that the arc-shaped elastic member 333 can also be used as a limiting torsion member to provide elastic force for the second gear 23 and the first gear 33, so that the main tooth gear 331 and the auxiliary tooth gear 332 can be staggered at a certain angle relative to each other, thereby eliminating the meshing backlash between the first gear 33 and the second gear 23, and reducing the knocking noise generated by the meshing of the first gear 33 and the second gear 23.

[0075] Furthermore, combined with Figure 3-Figure 8 As shown, the first gear 33 may further include an axial force applying member 334 , which is disposed on a side of the auxiliary gear 332 away from the main gear 331 and abuts against the auxiliary gear 332 .

[0076] Specifically, by arranging the axial force-applying member 334 on the side of the secondary gear 332 away from the main gear 331, the axial force-applying member 334 is abutted against the secondary gear 332, so that the axial force-applying member 334 can apply axial clamping force to the secondary gear 332, ensuring that the secondary gear 332 fits tightly when rotating on the main gear 331, eliminating the axial clearance between the main gear 331 and the secondary gear 332, thereby avoiding axial vibration of the secondary gear 332, improving the matching accuracy of the main gear 331 and the secondary gear 332, and further improving the reliability of the first gear 33, extending the service life of the first gear 33, and improving the NVH performance of the first gear 33 and even the balance shaft assembly 100.

[0077] Combination Figure 6 and Figure 8 As shown, the axial force member 334 is a disc spring. Specifically, the disc spring is a special spring that is conical in the axial direction and bears the load. After being deformed by the load, it stores a certain amount of potential energy. By setting the axial force member 334 as a disc spring, the disc spring can release part of the potential energy, that is, the disc spring can always be close to the auxiliary gear 332, providing an axial force for the auxiliary gear 332, so that the main gear 331 and the auxiliary gear 332 can maintain a fixed relative position in the axial direction, and improve the NVH performance of the first gear 33 and even the balance shaft assembly 100. The axial force member 334 can be easily obtained, and the structure is simple and reliable.

[0078] Furthermore, combined with Figure 6 and Figure 8As shown, the disc spring is provided with a first weight-reducing hole 3341, and there are a plurality of first weight-reducing holes 3341, and the plurality of first weight-reducing holes 3341 are spaced apart in the circumferential direction of the disc spring. Specifically, by providing a plurality of first weight-reducing holes 3341 on the disc spring, the weight of the disc spring can be reduced, and by providing a plurality of first weight-reducing holes 3341 at intervals in the circumferential direction of the disc spring, the distribution of the plurality of first weight-reducing holes 3341 on the disc spring can be made more uniform, so that, by providing a plurality of first weight-reducing holes 3341, the moment of inertia and dynamic torque of the active balancing shaft assembly 20 can be reduced, and the NVH performance of the balancing shaft assembly 100 can be improved.

[0079] Combination Figure 6-Figure 8 As shown, the first gear 33 may also include: a first positioning pin 335 and a second positioning pin 336, wherein the two ends of the first positioning pin 335 are respectively connected to the main gear 331 and the first end 3333, and the two ends of the second positioning pin 336 are respectively connected to the auxiliary gear 332 and the second end 3334. In this way, the main gear 331 and the first end 3333 of the arc-shaped elastic member 333 can be connected by the first positioning pin 335, so that the connection between the main gear 331 and the first end 3333 of the arc-shaped elastic member 333 is simpler, and the auxiliary gear 332 and the second end 3334 of the arc-shaped elastic member 333 can be connected by the second positioning pin 336, so that the connection between the auxiliary gear 332 and the second end 3334 of the arc-shaped elastic member 333 is simpler.

[0080] Furthermore, a first locating pin hole 3311 can be provided on the main tooth gear 331, and a second locating pin hole 3321 can be provided on the auxiliary tooth gear 332, and correspondingly, a third locating pin hole 3331 is opened on the first end 3333, and a fourth locating pin hole 3332 is opened on the second end 3334. By interference fitting one end of the first locating pin 335 with the first locating pin hole 3311 and passing the other end of the first locating pin 335 through the third locating pin hole 3331, the connection between the main tooth gear 331 and the first end 3333 can be achieved, and by interference fitting one end of the second locating pin 336 with the second locating pin hole 3321 and passing the other end of the second locating pin 336 through the fourth locating pin hole 3332, the connection between the auxiliary tooth gear 332 and the second end 3334 can be achieved. In this way, the connection between the arc-shaped elastic member 333 and the main tooth gear 331 and the auxiliary tooth gear 332 can be made simpler and more convenient.

[0081] Combination Figure 6-Figure 8As shown, the first gear 33 may also include: a first collar 337, a first boss 3312 is provided on the main gear 331, the first boss 3312 is coaxial with the main gear 331 and extends toward the auxiliary gear 332, a first mounting groove 3313 is provided on the first boss 3312, and a circular hole 3323 is provided on the auxiliary gear 332, and the circular hole 3323 is coaxial with the auxiliary gear 332, so that when the first end 3333 is connected to the main gear 331 and the second end 3334 is connected to the auxiliary gear After the wheel 332 is connected, the arc-shaped elastic member 333, the circular hole 3323 of the auxiliary gear 332, the axial force member 334 and the first clamping ring 337 are sequentially penetrated through the first boss 3312, and then the first clamping ring 337 is set in the first installation groove 3313, so that the first clamping ring 337 abuts against the side of the disc spring away from the auxiliary gear 332, thereby limiting the axial movement of the disc spring, thereby completing the assembly of the first gear 33 and ensuring the structural stability of the first gear 33.

[0082] Among them, the diameter of the circular hole 3323 is the same as the diameter of the first boss 3312, and the circular hole 3323 of the auxiliary gear 332 is loosely inserted on the first boss 3312 of the main gear 331, and the circular hole 3323 and the first boss 3312 are clearance-matched, which can not only ensure the coaxiality of the main gear 331 and the auxiliary gear 332, but also enable the auxiliary gear 332 to rotate freely, ensuring that the auxiliary gear 332 can be staggered at a certain angle relative to the main gear 331 under the action of the arc-shaped elastic member 333, thereby ensuring the normal operation of the first gear 33.

[0083] Furthermore, combined with Figure 6-Figure 8 As shown, a second boss 3322 is further provided on the auxiliary gear 332, and the diameter of the second boss 3322 is greater than the diameter of the first boss 3312. The second boss 3322 is coaxial with the auxiliary gear 332 and extends toward the main gear 331. A groove 3314 is provided on the main gear 331, and the diameter of the groove 3314 is the same as the diameter of the second boss 3322. In this way, when the first gear 33 is assembled, the second boss 3322 can also be extended into the groove 3314, and the second boss 3322 can be loosely matched with the groove 3314, so that not only the coaxiality of the main gear 331 and the auxiliary gear 332 can be further ensured, but also the auxiliary gear 332 can be freely rotated, so that the auxiliary gear 332 can be staggered relative to the main gear 331 by a certain angle under the action of the arc-shaped elastic member 333, thereby ensuring the normal operation of the first gear 33.

[0084] Combination Figure 5 As shown, a plurality of second weight-reducing holes 231 are provided on the second gear 23 . There are a plurality of second weight-reducing holes 231 , and the plurality of second weight-reducing holes 231 are spaced apart in the circumferential direction of the second gear 23 .

[0085] Specifically, by arranging a plurality of second weight-reducing holes 231 on the second gear 23, the weight of the second gear 23 can be reduced, and by arranging the plurality of second weight-reducing holes 231 at intervals in the circumferential direction of the second gear 23, the distribution of the plurality of second weight-reducing holes 231 on the second gear 23 can be more uniform. In this way, by arranging the plurality of second weight-reducing holes 231, the rotational inertia and dynamic torque of the active balancing shaft assembly 20 can be reduced, and the meshing noise between the second gear 23 and the crankshaft ring gear 301, and between the second gear 23 and the first gear 33 can be reduced, thereby improving the NVH performance of the balancing shaft assembly 100.

[0086] Further, the center of gravity of the second gear 23 falls on the rotation axis of the second gear 23 , and the center of gravity of the first gear 33 falls on the rotation axis of the first gear 33 .

[0087] Specifically, the second gear 23 is press-fitted onto the active balancing shaft 21, and the first active bearing 24 and the second active bearing 25 are also press-fitted onto the active balancing shaft 21. By making the center of gravity of the second gear 23 fall on the rotation axis of the second gear 23, it can be ensured that the second gear 23 has no unbalanced mass and the second gear 23 is dynamically balanced, thereby ensuring that the radial loads of the first active bearing 24 and the second active bearing 25 are consistent, and ensuring that the service life of the first active bearing 24 and the second active bearing 25 is consistent.

[0088] In addition, the first gear 33 is press-fitted onto the driven balancing shaft 31, and the first driven bearing 34 and the second driven bearing 35 are also press-fitted onto the driven balancing shaft 31. By making the center of gravity of the first gear 33 fall on the rotation axis of the first gear 33, it can be ensured that the first gear 33 has no unbalanced mass and the first gear 33 is dynamically balanced, thereby ensuring that the radial loads of the first driven bearing 34 and the second driven bearing 35 are consistent, and ensuring that the lifespans of the first driven bearing 34 and the second driven bearing 35 are consistent.

[0089] Combination Figure 2-Figure 4 As shown, the balancing shaft assembly 100 may include: a housing 10 , an active balancing shaft assembly 20 and a driven balancing shaft assembly 30 , wherein the active balancing shaft assembly 20 is rotatably disposed in the housing 10 , and the driven balancing shaft assembly 30 is rotatably disposed in the housing 10 .

[0090] Combination Figure 3-Figure 5 as well as Fig. 9 , Fig.10As shown, the active balancing shaft assembly 20 can mainly include: an active balancing shaft 21, a first active bearing 24 and a second gear 23, the second gear 23 is press-fitted on the active balancing shaft 21, and the first active bearing 24 is arranged on the active balancing shaft 21 at one end close to the second gear 23 and in front of the second gear 23, so that the rotation of the second gear 23 can drive the active balancing shaft 21 to rotate, so that the balancing block on the active balancing shaft 21 stirs the oil, and the oil splashes to the meshing part of the second gear 23 and the first gear 33, so as to avoid noise caused by insufficient lubrication, and the inner ring of the first active bearing 24 is interference-fitted with the active balancing shaft 21, which can play a role in supporting the active balancing shaft 21, reducing the friction coefficient of the active balancing shaft 21 during movement, and ensuring its rotation accuracy. Among them, the outer ring of the first active bearing 24 is also interference-fitted with the housing 10, so as to prevent the axial movement and circumferential rolling of the first active bearing 24.

[0091] Furthermore, by providing an active thrust step 16 on the housing 10, the active thrust step 16 is located behind the first active bearing 24, so that the outer ring of the first active bearing 24 can be limitedly matched with the active thrust step 16, so that the first active bearing 24 and even the active balancing shaft assembly 20 can be axially positioned to prevent the active balancing shaft assembly 20 from axially moving.

[0092] Combination Figure 3 , Figure 6 , Fig. 9 and Fig.11 As shown, the driven balancing shaft assembly 30 can mainly include: a driven balancing shaft 31, a first driven bearing 34 and a first gear 33. The first gear 33 is press-fitted on the driven balancing shaft 31. The first driven bearing 34 is arranged on the driven balancing shaft 31 at one end close to the first gear 33 and in front of the first gear 33. In this way, the rotation of the first gear 33 can drive the driven balancing shaft 31 to rotate, so that the balancing block on the driven balancing shaft 31 stirs the oil, and the oil splashes to the meshing part of the second gear 23 and the first gear 33, so as to avoid noise caused by insufficient lubrication. The inner ring of the first driven bearing 34 is in interference fit with the driven balancing shaft 31, which can play a role in supporting the driven balancing shaft 31, reduce the friction coefficient of the driven balancing shaft 31 during movement, and ensure its rotation accuracy. Among them, the outer ring of the first driven bearing 34 is also in interference fit with the housing 10, so as to prevent the axial movement and circumferential rolling of the first driven bearing 34.

[0093] It should be noted that when the first gear 33 is disposed on the driven balance shaft 31 , the main gear 331 can be located in front of the auxiliary gear 332 , or the auxiliary gear 332 can be located in front of the main gear 331 , which is not specifically limited here.

[0094] Furthermore, by providing a driven thrust step 17 on the housing 10, the driven thrust step 17 is located behind the first driven bearing 34, so that the outer ring of the first driven bearing 34 can be limitedly matched with the driven thrust step 17, so that the first driven bearing 34 and even the driven balancing shaft assembly 30 can be axially positioned to prevent the driven balancing shaft assembly 30 from axial stringing.

[0095] Combination Figure 3-Figure 5 as well as Fig. 9 , Fig.10 As shown, the active balancing shaft assembly 20 may further include: a second active bearing 25 and a second retaining ring 26. By arranging the second active bearing 25 at one end of the active balancing shaft 21 away from the second gear 23, the inner ring of the second active bearing 25 and the active balancing shaft 21 are in interference fit, which can play a role in supporting the active balancing shaft 21, reduce the friction coefficient of the active balancing shaft 21 during movement, and ensure its rotation accuracy. Among them, the outer ring of the second active bearing 25 is also in interference fit with the housing 10, which can prevent the second active bearing 25 from axial movement and circumferential rolling.

[0096] Furthermore, by providing a second mounting groove 18 on the housing 10, the second retaining ring 26 is disposed in the second mounting groove 18 and in front of the second active bearing 25, so that the second retaining ring 26 can be limitedly matched with the outer ring of the second active bearing 25, so that the second active bearing 25 and even the active balancing shaft assembly 20 can be axially positioned to prevent the active balancing shaft assembly 20 from axial stringing.

[0097] Combination Figure 3 , Figure 6 , Fig. 9 and Fig.11 As shown, the driven balancing shaft assembly 30 may further include: a second driven bearing 35 and a third clamping ring 36. The second driven bearing 35 is arranged at the end of the driven balancing shaft 31 away from the first gear 33. The inner ring of the second driven bearing 35 is in interference fit with the driven balancing shaft 31, which can support the driven balancing shaft 31, reduce the friction coefficient of the driven balancing shaft 31 during movement, and ensure its rotation accuracy. The outer ring of the second driven bearing 35 is also in interference fit with the housing 10, which can prevent the second driven bearing 35 from axial movement and circumferential rolling.

[0098] Furthermore, a third mounting groove 19 is provided on the housing 10, and a third clamping ring 36 is provided in the third mounting groove 19 and is located in front of the second driven bearing 35, so that the third clamping ring 36 can be limitedly matched with the outer ring of the second driven bearing 35, so that the third clamping ring 36 can be limitedly matched with the outer ring of the second driven bearing 35, so that the second driven bearing 35 and even the driven balancing shaft assembly 30 can be axially positioned to prevent the driven balancing shaft assembly 30 from axial stringing.

[0099] In some embodiments of the present invention, the first active bearing 24 , the second active bearing 25 , the first driven bearing 34 , and the second driven bearing 35 are all deep groove ball bearings. Specifically, the deep groove ball bearing has an axial thrust function, and the oil passage between the outer ring and the inner ring of the deep groove ball bearing is relatively large. By setting the first active bearing 24, the second active bearing 25, the first driven bearing 34 and the second driven bearing 35 as deep groove ball bearings, not only can the setting of thrust plates be avoided, the cost can be reduced, and the structure of the balancing shaft assembly 100 can be made simpler, but also the oil stirred up by the active balancing block 22 can be ensured to flow more smoothly to the second gear 23 through the oil unloading channel of the first active bearing 24, and the oil stirred up by the driven balancing block 32 can be ensured to flow more smoothly to the first gear 33 through the oil unloading channel of the first driven bearing 34, so that the second gear 23 and the first gear 33, as well as the meshing parts therebetween can be fully lubricated, the gear transmission noise of the balancing shaft assembly 100 can be reduced, and the NVH performance of the balancing shaft assembly 100 can be improved.

[0100] It should be noted that, among the active thrust step 16, the second retaining ring 26, the driven thrust step 17 and the third retaining ring 36 which are provided to ensure the stable installation of the first active bearing 24, the second active bearing 25, the first driven bearing 34 and the second driven shaft, the active thrust step 16 and the driven thrust step 17 have lower processing precision and lower processing cost, and the cost of the first retaining ring 337 and the second retaining ring 26 is also much lower than the cost of four thrust plates, thereby reducing costs and making the structure of the balancing shaft assembly 100 simpler.

[0101] In addition, in order to further reduce the meshing noise between the second gear 23 and the first gear 33, the present application strictly controls the center distance between the second gear 23 and the first gear 33, which is specifically achieved by strictly controlling the machining tolerance of the center distance between the mounting hole corresponding to the first active bearing 24 and the mounting hole corresponding to the first driven bearing 34, and the machining tolerance of the center distance between the mounting hole corresponding to the second active bearing 25 and the mounting hole corresponding to the second driven bearing 35, which will not be elaborated here.

[0102] Combination Figure 5 As shown, an active balancing block 22 is provided on the active balancing shaft 21 . The active balancing block 22 is located between the first active bearing 24 and the second active bearing 25 . The active balancing block 22 is semi-cylindrical, and the axis of the active balancing block 22 is colinear with the axis of the active balancing shaft 21 .

[0103] Specifically, an active balancing block 22 is provided on the active balancing shaft 21, and the active balancing block 22 is located between the first active bearing 24 and the second active bearing 25. In this way, the driven balancing block 32 can stir the oil in the housing 10, so that the oil enters the first active bearing 24 and the second active bearing 25, and enters the second gear 23 through the first active bearing 24, so that the first active bearing 24 and the second active bearing 25 can be lubricated, and ablation and abnormal wear of the first active bearing 24 and the second active bearing 25 can be avoided, and the meshing portion between the second gear 23 and the first gear 33 can be lubricated, which can attenuate the meshing noise and reduce friction loss and wear.

[0104] Furthermore, by making the active balancing block 22 semi-cylindrical, the upper plane of the active balancing block 22 passes through the rotation axis of the driven balancing shaft 31, and the axis of the active balancing block 22 is colinear with the axis of the active balancing shaft 21, the rotation of the active balancing shaft assembly 20 can be made smoother while ensuring the oil stirring ability of the active balancing block 22.

[0105] In some embodiments of the utility model, the active balancing block 22 and the active balancing shaft 21 are integrally formed as a ductile iron structure. Specifically, in order to adapt to the arrangement of the second gear 23, the first active bearing 24 and the second active bearing 25 on the active balancing shaft 21, the active balancing shaft 21 is provided with a plurality of steps with different diameters and smooth transitions. By forming the active balancing block 22 and the active balancing shaft 21 as an integrally formed ductile iron structure, not only can the structural strength of the active balancing block 22 and the active balancing shaft 21 be improved, the connection strength between the active balancing block 22 and the active balancing shaft 21 can be improved, thereby improving the structural reliability of the active balancing shaft assembly 20, but also the production process of the active balancing block 22 and the active balancing shaft 21 can be simplified, thereby reducing the manufacturing cost.

[0106] Combination Figure 6 As shown, a driven balancing weight 32 is provided on the driven balancing shaft 31 . The driven balancing weight 32 is located between the first driven bearing 34 and the second driven bearing 35 . The driven balancing weight 32 is semi-cylindrical, and the axis of the driven balancing weight 32 is colinear with the axis of the driven balancing shaft 31 .

[0107] Specifically, by arranging a driven balancing weight 32 on the driven balancing shaft 31, the driven balancing weight 32 is located between the first driven bearing 34 and the second driven bearing 35, so that the driven balancing weight 32 can stir the oil in the housing 10, so that the oil enters the first driven bearing 34 and the second driven bearing 35, and enters the first gear 33 through the first driven bearing 34, so that the first driven bearing 34 and the second driven bearing 35 can be lubricated, and the ablation and abnormal wear of the first driven bearing 34 and the second driven bearing 35 can be avoided, and the meshing part between the first gear 33 and the second gear 23 can be lubricated, which can attenuate the meshing noise and reduce friction loss and wear.

[0108] Furthermore, by making the driven balancing block 32 semi-cylindrical, the upper plane of the driven balancing block 32 passes through the rotation axis of the driven balancing shaft 31, and the axis of the driven balancing block 32 is colinear with the axis of the driven balancing shaft 31, the rotation of the driven balancing shaft assembly 30 can be made smoother while ensuring the oil stirring ability of the driven balancing block 32.

[0109] In some embodiments of the utility model, the driven balancing block 32 and the driven balancing shaft 31 are integrally formed spheroidal cast iron structures. Specifically, in order to adapt to the arrangement of the first gear 33, the first driven bearing 34 and the second driven bearing 35 on the driven balancing shaft 31, a plurality of steps with different diameters and smooth transitions are arranged on the driven balancing shaft 31. By forming the driven balancing block 32 and the driven balancing shaft 31 as an integrally formed spheroidal cast iron structure, not only the structural strength of the driven balancing block 32 and the driven balancing shaft 31 can be improved, the connection strength of the driven balancing block 32 and the driven balancing shaft 31 can be improved, thereby improving the structural reliability of the driven balancing shaft assembly 30, but also the production process of the driven balancing block 32 and the driven balancing shaft 31 can be simplified, thereby reducing the manufacturing cost.

[0110] Combination Figure 5 and Figure 6 As shown, the active balancing shaft 21 is provided with an active reinforcing rib 27, which is located on the side of the active balancing shaft 21 away from the active balancing block 22. The active reinforcing rib 27 is extended in the axial direction of the active balancing shaft 21 and has the same length as the active balancing block 22. In this way, the structural strength and structural rigidity of the active balancing shaft 21 can be enhanced by the provision of the active reinforcing rib 27, thereby improving the structural reliability of the active balancing shaft assembly 20.

[0111] In addition, a driven reinforcing rib 37 is provided on the driven balancing shaft 31. The driven reinforcing rib 37 is located on the side of the driven balancing shaft 31 away from the driven balancing block 32. The driven reinforcing rib 37 is extended in the axial direction of the driven balancing shaft 31 and has the same length as the driven balancing block 32. In this way, the structural strength and structural rigidity of the driven balancing shaft 31 can be enhanced by the setting of the driven reinforcing rib 37, thereby improving the structural reliability of the driven balancing shaft assembly 30.

[0112] In a specific embodiment of the present invention, the active balancing block 22 and the driven balancing block 32 have the same length, and the thickness of the active reinforcing rib 27 and the driven reinforcing rib 37 can be set to 6 mm, and the height can be set to 8 mm.

[0113] Combination Figure 2-Figure 4 As shown, the shell 10 may include an upper shell 11, a lower shell 12 and a first fastener 13. The upper shell 11 and the lower shell 12 are arranged opposite to each other. A plurality of first through-holes 111 are arranged on the upper shell 11, and a plurality of second through-holes 121 are arranged on the lower shell 12. The plurality of first through-holes 111 and the plurality of second through-holes 121 correspond to each other one by one. The first fastener 13 simultaneously penetrates the first through-holes 111 and the second through-holes 121 to connect and fix the upper shell 11 and the lower shell 12. The upper shell 11 and the lower shell 12 are respectively integrally made structural parts.

[0114] Specifically, the housing 10 includes an upper housing 11 and a lower housing 12, a plurality of first through-holes 111 are provided on the upper housing 11, and a plurality of second through-holes 121 are provided on the lower housing 12, and the plurality of first through-holes 111 and the plurality of second through-holes 121 correspond to each other one by one. In this way, the active balancing shaft assembly 20 and the driven balancing shaft assembly 30 can be firstly arranged in the lower housing 12, and then the upper housing 11 is covered on the lower housing 12, so that the upper housing 11 and the lower housing 12 are arranged relative to each other, and finally the first fastener 13 is simultaneously penetrated with the first through-hole 111 and the second through-hole 121, and the upper housing 11 and the lower housing 12 are connected and fixed, so that the assembly of the balancing shaft assembly 100 can be realized, and the assembly of the balancing shaft assembly 100 can be made simpler and more efficient.

[0115] Furthermore, the upper shell 11 can be set as an integrally manufactured structural member, and the lower shell 12 can be set as an integrally manufactured structural member, which can not only simplify the production process of the upper shell 11 and the lower shell 12, improve the production efficiency of the shell 10, and reduce the production cost of the shell 10, but also make the structural strength of the upper shell 11 and the lower shell 12 higher, and make the structure of the shell 10 more stable and reliable. Among them, the material of the upper shell 11 includes but is not limited to aluminum alloy, and the material of the lower shell 12 is but is not limited to aluminum alloy.

[0116] Combination Figure 2-Figure 4As shown, the upper shell 11 is provided with a fifth locating pin hole 112, and there are two fifth locating pin holes 112 and they are diagonally distributed on the upper shell 11; the lower shell 12 is provided with a sixth locating pin hole 122, and there are two sixth locating pin holes 122 and they correspond one to one with the two fifth locating pin holes 112; the shell 10 may also include: a third locating pin 14, which is arranged in this way. When the upper shell 11 and the lower shell 12 are arranged relative to each other to connect and fix the two, the third locating pin 14 can be positioned and matched with the fifth locating pin hole 112 and the sixth locating pin hole 122 at the same time, so that the upper shell 11 and the lower shell 12 can be quickly in the correct assembly position, and the positioning accuracy of the upper shell 11 and the lower shell 12 can be improved. After the shell 10 is disassembled and reassembled, a higher cylindricality of the bearing hole can also be obtained, which can further improve the assembly efficiency of the shell 10 and even the balance shaft assembly 100.

[0117] Combination Figure 3 and Figure 4 As shown, a locking pin hole 123 is provided at the bottom of the lower shell 12, the active balancing shaft assembly 20 includes an active balancing block 22, the driven balancing shaft assembly 30 includes a driven balancing block 32, and a phase positioning hole 221 is provided on the active balancing block 22 and / or the driven balancing block 32. The shell 10 may also include: a locking pin 15, and the locking pin 15 selectively penetrates the locking pin hole 123 and the phase positioning hole 221 at the same time.

[0118] Specifically, by setting a locking pin hole 123 at the bottom of the lower shell 12, a phase positioning hole 221 is set on the active balancing block 22 and / or the driven balancing block 32. In this way, after the balancing shaft assembly is set on the shell 10 and the preliminary assembly of the balancing shaft assembly 100 is completed, the locking pin 15 can be passed through the locking pin hole 123 and inserted into the phase positioning hole 221, so that the active balancing block 22 and the driven balancing block 32 can be locked to a vertical downward position, and the phase of the active balancing block 22 and the driven balancing block 32 can be positioned, which not only ensures the normal operation of the balancing shaft assembly 100, but also facilitates assembly and has high assembly efficiency.

[0119] Furthermore, after completing the assembly of the balance shaft assembly 100, the locking pin 15 can be removed, and the locking pin hole 123 can also be used as an oil hole, so that the oil in the oil pan 400 and the oil in the housing 10 can be adjusted to each other. On the one hand, the oil in the oil pan 400 can enter the housing 10 through the locking pin hole 123 to replenish the oil inside the housing 10. On the other hand, the oil in the housing 10 can also flow out through the locking pin hole 123, thereby ensuring that the amount of oil inside the housing 10 is appropriate, and the working performance of the balance shaft assembly 100 can be improved.

[0120] Combination Figure 1As shown, the engine 1000 according to the present invention may mainly include: the above-mentioned balance shaft assembly 100. Specifically, by applying the balance shaft assembly 100 to the engine 1000, the NVH performance of the engine 1000 may be improved, and the comprehensive performance of the engine 1000 may be improved.

[0121] Combination Figure 1 and Figure 3 As shown, the engine 1000 may further include: a cylinder block 200 and an oil pan 400, wherein the cylinder block 200 is provided with a plurality of cylinders spaced apart in the front-rear direction, wherein the symmetry plane of the plurality of cylinders in the left-right direction is a first plane, wherein the cylinder block 200 is provided with a crankshaft 300, wherein the crankshaft 300 is provided with a crankshaft gear ring 301, wherein the balance shaft assembly 100 is transmission-connected to the crankshaft gear ring 301, wherein the oil pan 400 is provided on the lower surface of the cylinder block 200, wherein the balance shaft assembly 100 is provided in the oil pan 400, and wherein the center of gravity of the active balance shaft assembly 20 and the center of gravity of the driven balance shaft assembly 30 are symmetrical about the first plane.

[0122] Specifically, a cylinder block 200 is provided at the lower part of the engine 1000, and a bearing hole is provided at the lower part of the cylinder block 200 to support the bearing part of the crankshaft 300, and an oil pan 400 for storing oil inside is installed and covered on the outer periphery. By providing a third through hole 113 on the housing 10, the second fastener 40 penetrates the third through hole 113 and is connected and fixed to the lower surface of the cylinder block 200, and the balance shaft assembly 100 is provided in the oil pan 400, and the balance shaft assembly 100 is partially immersed in lubricating oil, so that the installation and setting of the balance shaft assembly 100 inside the engine 1000 can be realized.

[0123] Furthermore, by arranging a crankshaft gear ring 301 on the crankshaft 300 and connecting the balance shaft assembly 100 and the crankshaft gear ring 301 in a transmission manner, the rotational torque of the crankshaft 300 can be transmitted to the balance shaft assembly 100 via the crankshaft gear ring 301, thereby driving the balance shaft assembly 100. The speed ratio between the crankshaft gear ring 301 and the second gear 23 can be set to 1:2, and the first gear 33 and the second gear 23 have the same rotation speed, so that the rotation speed of the active balance shaft assembly 20 is twice the rotation speed of the crankshaft 300, and the rotation speed of the driven balance shaft assembly 30 is twice the rotation speed of the crankshaft 300.

[0124] Furthermore, a plurality of cylinders are arranged in the cylinder body 200 at intervals in the front-to-back direction, and a symmetry plane of the plurality of cylinders in the left-to-right direction is defined as a first plane. By making the center of gravity of the active balancing shaft assembly 20 and the center of gravity of the driven balancing shaft assembly 30 symmetrical about the first plane, on the one hand, the components of the rotational inertia force generated by the unbalanced masses of the active balancing shaft assembly 20 and the driven balancing shaft assembly 30 in the up-down direction can be made the same in magnitude and direction, thereby offsetting the second-order reciprocating inertia force generated by the movement of the piston-connecting rod assembly and reducing the noise and vibration of the engine 1000. On the other hand, the components of the rotational inertia force generated by the unbalanced masses of the active balancing shaft assembly 20 and the driven balancing shaft assembly 30 in the horizontal direction can be made the same in magnitude and opposite in direction, thereby offsetting each other, thereby eliminating the second-order reciprocating inertia force generated by the movement of the piston-connecting rod assembly inside the engine 1000, avoiding the vibration caused by the second-order reciprocating inertia force from being transmitted to the vehicle body through the engine 1000 suspension, and improving the ride comfort of the entire vehicle.

[0125] Among them, by making the second gear 23 mesh with the crankshaft ring gear 301, the transmission connection between the balance shaft assembly 100 and the crankshaft ring gear 301 can be achieved. In order to reduce the gear meshing noise between the balance shaft assembly 100 and the crankshaft ring gear 301, the center distance between the second gear 23 and the crankshaft ring gear 301 can be controlled, and then the tooth side clearance between the second gear 23 and the crankshaft ring gear 301 can be controlled within a smaller and reasonable range, thereby reducing the knocking energy of the meshing of the second gear 23 and the crankshaft ring gear 301 and attenuating the noise.

[0126] Specifically, after the housing 10 is assembled to the cylinder block 200, the second fastener 40 is tightened to cause the housing 10 to be compressed and deformed, further affecting the center distance between the second gear 23 and the crankshaft gear ring 301 and affecting the tooth side clearance. In addition, the balancing assembly is arranged in the oil pan 400. When the engine 1000 is running, the temperature range in the oil pan 400 is -40℃~+140℃. The cylinder block 200, the housing 10, the second gear 23 and the first gear 33 will all undergo thermal expansion deformation and contraction, which will affect the center distance between the second gear 23 and the crankshaft gear ring 301 and affect the tooth side clearance. Considering the above factors, the minimum assembly tooth side clearance between the second gear 23 and the crankshaft gear ring 301 is set to 0.04mm.

[0127] Furthermore, by assembling two hollow cylindrical pins on the cylinder body 200 of the engine 1000, the crank-connecting rod piston mechanism is positioned to the top dead center of compression of a cylinder, and two waist-shaped holes 114 concentric with the third through hole 113 are provided on the side of the housing 10 close to the second gear 23 and the first gear 33. The two waist-shaped holes 114 can allow the balance shaft assembly 100 to move in a small range relative to the cylinder body 200, so that the tooth side clearance between the second gear 23 and the crankshaft gear ring 301 can be adjusted to a set range by pushing the balance shaft assembly 100 left and right, thereby improving the NVH performance of the engine 1000 assembly.

[0128] Combination Figure 1 As shown, there are four cylinders and they are the first cylinder 201, the second cylinder 202, the third cylinder 203 and the fourth cylinder 204 in the front-to-back direction, the symmetry plane of the second cylinder 202 and the third cylinder 203 in the front-to-back direction is the second plane, the active balancing shaft assembly 20 includes an active balancing block 22, the driven balancing shaft assembly 30 includes a driven balancing block 32, and the center of gravity of the active balancing block 22 and the center of gravity of the driven balancing block 32 are both located on the second plane.

[0129] Specifically, the symmetry plane of the second cylinder 202 and the third cylinder 203 in the front-to-back direction is defined as the second plane. By locating the center of gravity of the active balancing block 22 and the center of gravity of the driven balancing block 32 in the first plane, the center of gravity of the entire engine 1000 can be made to fall on the first plane. In this way, the balancing shaft assembly 100 can be set in the middle position in the front-to-back direction, and the setting position of the balancing shaft assembly 100 can be optimized, thereby further improving the NVH performance of the engine 1000.

[0130] In addition, the center of gravity of the active balancing block 22 and the center of the driven balancing block 32 can be made symmetrical about the first plane. In this way, on the one hand, the components of the rotational inertia force generated by the unbalanced masses of the active balancing block 22 and the driven balancing block 32 in the vertical direction can be made the same in magnitude and direction, thereby further reducing the noise and vibration of the engine 1000. On the other hand, the components of the rotational inertia force generated by the unbalanced masses of the active balancing block 22 and the driven balancing block 32 in the horizontal direction can be made the same in magnitude and opposite in direction, thereby canceling each other out, thereby further avoiding the vibration caused by the second-order reciprocating inertia force from being transmitted to the vehicle body through the engine 1000 suspension, thereby improving the ride comfort of the entire vehicle.

[0131] The power assembly according to the present invention may mainly include: the above-mentioned engine 1000. Specifically, by applying the engine 1000 to the power assembly, the NVH performance of the power assembly can be guaranteed and the comprehensive performance of the power assembly can be improved.

[0132] The vehicle according to the present invention may mainly include: the above-mentioned engine 1000 or the above-mentioned power assembly, so as to improve the running performance of the vehicle, improve the user experience, and improve the product competitiveness of the vehicle.

[0133] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the referred device or element must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as a limitation on the present invention.

[0134] In the description of this specification, the description with reference to the terms "one embodiment", "some embodiments", "illustrative embodiments", "examples", "specific examples", or "some examples" means that the specific features, structures, materials, or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the utility model. In this specification, the schematic expressions of the above terms do not necessarily refer to the same embodiment or example.

[0135] Although the embodiments of the present invention have been shown and described, those skilled in the art will appreciate that various changes, modifications, substitutions and variations may be made to the embodiments without departing from the principles and spirit of the present invention, and that the scope of the present invention is defined by the claims and their equivalents.

Claims

1. A balance shaft assembly, characterized in that: include: A first gear (33), the first gear (33) comprising: a main gear (331), a secondary gear (332) and an arc-shaped elastic member (333), the main gear (331) and the secondary gear (332) being arranged in a front-to-rear direction, the arc-shaped elastic member (333) being arranged around the axis of the first gear (33), and having a first end (3333) and a second end (3334) being arranged at intervals around the axis of the first gear (33), the first end (3333) being connected to the main gear (331), and the second end (3334) being connected to the secondary gear (332).

2. The balance shaft assembly according to claim 1, characterized in that: The central angle of the arc-shaped elastic member (333) is α, and α satisfies the relationship: α≥270°.

3. The balance shaft assembly according to claim 1, characterized in that: The first gear (33) further comprises: a first positioning pin (335) and a second positioning pin (336), wherein two ends of the first positioning pin (335) are respectively connected to the main gear (331) and the first end (3333), and two ends of the second positioning pin (336) are respectively connected to the auxiliary gear (332) and the second end (3334).

4. The balance shaft assembly according to claim 3, characterized in that: The main gear (331) is provided with a first positioning pin hole (3311), the auxiliary gear (332) is provided with a second positioning pin hole (3321), the first end (3333) is provided with a third positioning pin hole (3331), the second end (3334) is provided with a fourth positioning pin hole (3332), one end of the first positioning pin (335) is interference-fitted with the first positioning pin hole (3311) and the other end is penetrated by the third positioning pin hole (3331), one end of the second positioning pin (336) is interference-fitted with the second positioning pin hole (3321) and the other end is penetrated by the fourth positioning pin hole (3332).

5. The balance shaft assembly according to claim 1, characterized in that: The first gear (33) further comprises an axial force applying member (334), wherein the axial force applying member (334) is arranged on a side of the auxiliary gear (332) away from the main gear (331) and is in contact with the auxiliary gear (332).

6. The balance shaft assembly according to claim 5, characterized in that: The axial force applying member (334) is a disc spring.

7. The balance shaft assembly according to claim 6, characterized in that: The disc spring is provided with a first weight-reducing hole (3341), and there are a plurality of the first weight-reducing holes (3341), which are spaced apart in the circumferential direction of the disc spring.

8. The balance shaft assembly according to claim 5, characterized in that: The first gear (33) further comprises: a first clamping ring (337); a first boss (3312) is provided on the main gear (331); the first boss (3312) is coaxial with the main gear (331) and extends toward the auxiliary gear (332); a first mounting groove (3313) is provided on the first boss (3312); a circular hole (3323) is provided on the auxiliary gear (332); the circular hole (3323) is coaxial with the auxiliary gear (332); the arc-shaped elastic member (333), the circular hole (3323), the axial force member (334) and the first clamping ring (337) are sequentially penetrated through the first boss (3312); the first clamping ring (337) is arranged in the first mounting groove (3313); and the first clamping ring (337) abuts against a side of the axial force member (334) facing away from the auxiliary gear (332).

9. The balance shaft assembly according to claim 8, characterized in that: The secondary gear (332) is also provided with a second boss (3322), the diameter of the second boss (3322) is greater than the diameter of the first boss (3312), the second boss (3322) is coaxial with the secondary gear (332) and extends toward the primary gear (331), the primary gear (331) is provided with a groove (3314), the diameter of the groove (3314) is the same as the diameter of the second boss (3322), and the second boss (3322) extends into the groove (3314) and is clearance-matched with the groove (3314).

10. The balance shaft assembly according to claim 1, characterized in that: The invention also comprises a second gear (23), wherein the second gear (23) is respectively meshed with the main gear (331) and the auxiliary gear (332), and the second gear (23) is provided with a plurality of second weight-reducing holes (231). The second weight-reducing holes (231) are multiple, and the plurality of second weight-reducing holes (231) are spaced apart in the circumferential direction of the second gear (23).

11. The balance shaft assembly according to claim 1, characterized in that: The invention comprises a second gear (23), wherein the second gear (23) is respectively meshed with the main gear (331) and the auxiliary gear (332), the center of gravity of the second gear (23) falls on the rotation axis of the second gear (23), and the center of gravity of the first gear (33) falls on the rotation axis of the first gear (33).

12. The balance shaft assembly according to claim 1, characterized in that: include: A second gear (23), a housing (10), an active balancing shaft assembly (20) and a driven balancing shaft assembly (30), wherein the second gear (23) is respectively meshed with the main gear (331) and the auxiliary gear (332), the active balancing shaft assembly (20) is rotatably disposed in the housing (10) and comprises: an active balancing shaft (21), a first active bearing (24) and the second gear (23), the second gear (23) being disposed on the active balancing shaft (21), the first active bearing (24) being disposed on one end of the active balancing shaft (21) close to the second gear (23) and being located in front of the second gear (23), and an active thrust step (16) being disposed on the housing (10), the active thrust step (16) being located behind the first active bearing (24) and being limitedly matched with the first active bearing (24); The driven balancing shaft assembly (30) is rotatably disposed in the housing (10) and comprises: a driven balancing shaft (31), a first driven bearing (34) and the first gear (33); the first gear (33) is disposed on the driven balancing shaft (31); the first driven bearing (34) is disposed on one end of the driven balancing shaft (31) close to the first gear (33) and is located in front of the first gear (33); a driven thrust step (17) is disposed on the housing (10); the driven thrust step (17) is located behind the first driven bearing (34) and is limitedly matched with the first driven bearing (34).

13. The balance shaft assembly according to claim 12, characterized in that: The active balancing shaft assembly (20) further comprises: a second active bearing (25) and a second clamping ring (26); the second active bearing (25) is arranged at an end of the active balancing shaft (21) away from the second gear (23); a second mounting groove (18) is arranged on the housing (10); the second clamping ring (26) is arranged in the second mounting groove (18) and is located in front of the second active bearing (25); the second clamping ring (26) and the second active bearing (25) are limitedly matched; The driven balancing shaft assembly (30) further comprises: a second driven bearing (35) and a third retaining ring (36); the second driven bearing (35) is arranged at an end of the driven balancing shaft (31) away from the first gear (33); a third mounting groove (19) is arranged on the housing (10); the third retaining ring (36) is arranged in the third mounting groove (19) and is located in front of the second driven bearing (35); the third retaining ring (36) is limitedly matched with the second driven bearing (35).

14. The balance shaft assembly according to claim 13, characterized in that: The first active bearing (24), the second active bearing (25), the first driven bearing (34) and the second driven bearing (35) are all deep groove ball bearings.

15. The balance shaft assembly according to claim 13, characterized in that: An active balancing block (22) is arranged on the active balancing shaft (21), the active balancing block (22) is located between the first active bearing (24) and the second active bearing (25), the active balancing block (22) is semi-cylindrical, and the axis of the active balancing block (22) is colinear with the axis of the active balancing shaft (21); A driven balancing weight (32) is arranged on the driven balancing shaft (31), and the driven balancing weight (32) is located between the first driven bearing (34) and the second driven bearing (35). The driven balancing weight (32) is semi-cylindrical, and the axis of the driven balancing weight (32) is colinear with the axis of the driven balancing shaft (31).

16. The balance shaft assembly according to claim 15, characterized in that: The active balancing block (22) and the active balancing shaft (21) are integrally manufactured spheroidal cast iron structural parts, and the driven balancing block (32) and the driven balancing shaft (31) are integrally manufactured spheroidal cast iron structural parts.

17. The balance shaft assembly according to claim 15, characterized in that: An active reinforcing rib (27) is provided on the active balancing shaft (21), the active reinforcing rib (27) is located on a side of the active balancing shaft (21) away from the active balancing block (22), the active reinforcing rib (27) is extended in the axial direction of the active balancing shaft (21) and has the same length as the active balancing block (22); A driven reinforcing rib (37) is provided on the driven balancing shaft (31), and the driven reinforcing rib (37) is located on a side of the driven balancing shaft (31) away from the driven balancing weight (32). The driven reinforcing rib (37) is extended in the axial direction of the driven balancing shaft (31) and has the same length as the driven balancing weight (32).

18. The balance shaft assembly according to claim 12, characterized in that: The shell (10) comprises an upper shell (11), a lower shell (12) and a first fastener (13); the upper shell (11) and the lower shell (12) are arranged relative to each other; the upper shell (11) is provided with a plurality of first through-holes (111); the lower shell (12) is provided with a plurality of second through-holes (121); the plurality of first through-holes (111) and the plurality of second through-holes (121) correspond to each other one by one; the first fastener (13) simultaneously penetrates the first through-holes (111) and the second through-holes (121) to connect and fix the upper shell (11) and the lower shell (12); the upper shell (11) and the lower shell (12) are respectively integrally made structural parts.

19. The balance shaft assembly according to claim 18, characterized in that: The upper shell (11) is provided with a fifth positioning pin hole (112), the number of the fifth positioning pin holes (112) being two and being distributed diagonally on the upper shell (11); the lower shell (12) is provided with a sixth positioning pin hole (122), the number of the sixth positioning pin holes (122) being two and corresponding one-to-one with the two fifth positioning pin holes (112); the shell (10) further comprises: a third positioning pin (14), the third positioning pin (14) being positioned and matched with the fifth positioning pin hole (112) and the sixth positioning pin hole (122) at the same time.

20. The balance shaft assembly according to claim 19, characterized in that: A locking pin hole (123) is provided below the lower shell (12); the active balancing shaft assembly (20) includes an active balancing block (22); the driven balancing shaft assembly (30) includes a driven balancing block (32); a phase positioning hole (221) is provided on the active balancing block (22) and / or the driven balancing block (32); the shell (10) further includes: a locking pin (15); the locking pin (15) selectively penetrates the locking pin hole (123) and the phase positioning hole (221) at the same time.

21. An engine, characterized in that: include: The balancing shaft assembly (100) according to any one of claims 1 to 20.

22. The engine according to claim 21, characterized in that Also includes: A cylinder body (200), wherein a plurality of cylinders are arranged in a front-to-rear direction at intervals, wherein a symmetric plane of the plurality of cylinders in a left-to-right direction is a first plane, wherein a crankshaft (300) is arranged in the cylinder body (200), wherein the crankshaft (300) is provided with a crankshaft gear ring (301), and wherein the balance shaft assembly (100) is drivingly connected to the crankshaft gear ring (301); An oil pan (400) is disposed on the lower surface of the cylinder block (200); the balancing shaft assembly (100) is disposed in the oil pan (400) and comprises: an active balancing shaft assembly (20) and a driven balancing shaft assembly (30); the center of gravity of the active balancing shaft assembly (20) and the center of gravity of the driven balancing shaft assembly (30) are symmetrical about the first plane.

23. The engine according to claim 22, characterized in that There are four cylinders, which are respectively a first cylinder (201), a second cylinder (202), a third cylinder (203) and a fourth cylinder (204) in the front-to-back direction; a symmetry plane between the second cylinder (202) and the third cylinder (203) in the front-to-back direction is a second plane; the active balancing shaft assembly (20) includes an active balancing block (22); the driven balancing shaft assembly (30) includes a driven balancing block (32); the center of gravity of the active balancing block (22) and the center of gravity of the driven balancing block (32) are both located on the second plane.

24. A powertrain, characterized in that: include: The engine (1000) of any one of claims 22-23.

25. A vehicle, characterized in that: include: The engine (1000) as claimed in any one of claims 22 to 23 or the powertrain as claimed in claim 24.

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