Elastic coupling assembly and hybrid power system

Abstract

The invention belongs to the technical field of power transmission, and particularly relates to an elastic coupling assembly and a hybrid power system.The elastic coupling assembly comprises a straight-tooth spline hollow shaft with one side used for abutting against or being connected with a shaft sleeve and the inner circle of the other side provided with a straight-tooth internal spline; a straight tooth external spline is arranged on the outer circle of one side of the straight tooth coupling, the straight tooth external spline is connected with the straight tooth internal spline in a meshed mode, and a first straight tooth used for being connected with the output end of the output motor in a meshed mode is arranged on the outer surface of the other side of the straight tooth coupling; the bearing assembly is used for being arranged between the radial outer surface of the shaft sleeve and the radial inner wall of the casing, and the elastic coupling assembly is fixed in the casing through the bearing assembly; and the wave spring washer is positioned between the axial side of the bearing assembly and the axial inner wall of the casing. The wave spring washer is arranged between the bearing assembly and the casing, axial tension is transferred to the casing, impact load is absorbed in an elastic deformation mode, and the axial force peak value is reduced.

Description

Technical Field

[0001] This invention belongs to the field of power transmission technology, specifically relating to a flexible coupling assembly and a hybrid power system. Background Technology

[0002] In a hybrid power system, the power generated by the engine drives the electric motor to generate electricity and output electrical energy. Specifically, the mechanical output shaft of the power turbine can be connected to the input shaft of the motor so that the output shaft of the power turbine rotates and the output motor shaft rotates to output electrical energy.

[0003] However, the engine operation generates a very large axial tensile force, such as 603N, which is transmitted to the high-speed motor through the shaft. Therefore, a reasonable coupling scheme needs to be designed to mitigate this axial tensile force. Summary of the Invention

[0004] The present invention addresses the above-mentioned technical problems by providing a flexible coupling assembly and a hybrid power system.

[0005] A flexible coupling assembly, the flexible coupling assembly comprising:

[0006] A spur-tooth hollow shaft, the side of which is closer to the engine is used to abut or connect with a bushing fitted around the engine output shaft of the engine, and the inner circle of the other side of the spur-tooth hollow shaft away from the engine has a spur-tooth internal spline;

[0007] A spur gear coupling has a spur external spline on its outer circumference away from the output motor. The spur gear coupling extends from the side away from the output motor into the interior of the spur spline hollow shaft on the other side away from the engine. The spur external spline meshes with the spur internal spline. The outer surface of the spur gear coupling near the output motor has a first spur tooth for meshing with the output end of the output motor.

[0008] A bearing assembly is provided, which is disposed between the radial outer surface of the bushing and the radial inner wall of the casing, and fixes the flexible coupling assembly inside the casing. The casing is disposed between the engine and the output motor. One end of the casing is fixedly connected to the housing of the engine, and the other end of the casing is fixedly connected to the housing of the output motor.

[0009] A wave spring washer is located between the axial side of the bearing assembly and the axial inner wall of the casing.

[0010] Optionally, there is a gap between the outer circle of the wave spring washer and the radial direction of the casing.

[0011] Optionally, the elastic modulus of the wave spring washer is 210.8 N / mm, the working load of the wave spring washer is 1274.9 N, and the pre-compression of the wave spring washer is 2 mm to 3 mm.

[0012] Optionally, the uncompressed thickness of the wave spring washer is 4 mm.

[0013] Optionally, the spur gear coupling is provided with a coupling through hole extending through both sides, and the coupling through hole communicates with the interior of the spur gear spline hollow shaft.

[0014] Optionally, the spur spline hollow shaft has a hollow shaft step extending towards the shaft center on the side near the engine. The end face of the hollow shaft step near the engine abuts against the bushing, and the end face away from the engine abuts against a first locking nut. The first locking nut is used to thread a connection with the engine output shaft passing through the hollow shaft step, and the end face of the hollow shaft step near the engine abuts against the bushing through the first locking nut.

[0015] A hybrid power system includes an engine and an output motor, wherein the engine and the output motor are connected via the flexible coupling assembly;

[0016] The power turbine output shaft of the engine is connected to a bushing via a spur spline or interference fit, and the bushing abuts against or is connected to the side of the spur spline hollow shaft near the engine.

[0017] The output end of the output motor is provided with a second straight tooth, which meshes with the first straight tooth of the straight tooth coupling.

[0018] Optionally, the spur spline hollow shaft has a hollow shaft step extending towards the shaft center on the side near the engine. The outer surface of one side of the bushing has a platform that mates with the hollow shaft step. The platform extends into the side of the spur spline hollow shaft near the engine. The end of the power turbine output shaft away from the engine passes through the hollow shaft step from the side of the spur spline hollow shaft near the engine and is threaded to a first locking nut on the other side of the hollow shaft step away from the engine, thereby achieving a fixed connection with the spur spline hollow shaft. The first locking nut abuts the end face of the spur spline hollow shaft near the engine against the end face of the bushing.

[0019] Optionally, the shaft end of the output motor is connected to a motor spline, and the inner circle of the motor spline is provided with the second spur tooth.

[0020] Optionally, the hybrid power system further includes a casing disposed between the engine and the output motor, one end of the casing being fixedly connected to the housing of the engine, and the other end of the casing being fixedly connected to the housing of the output motor;

[0021] The flexible coupling assembly is fixed to the housing by a bearing assembly disposed outside the bushing.

[0022] Optionally, the casing is provided with a stepped mounting cavity extending along the axial direction. The mounting cavity includes an open section for pressing in the bearing steel sleeve and forms an annular stepped surface in the hole.

[0023] The bearing assembly includes a bearing body and a bearing sleeve. The outer ring of the bearing body is installed in the inner hole of the bearing sleeve, and the inner ring of the bearing body is fitted onto the bushing. The outer circle of the bearing sleeve is pressed into the mounting cavity. A wave spring washer abuts between the end face of the bearing sleeve near the engine and the annular stepped surface. A second locking nut is threaded onto the bushing on the other side of the bearing sleeve away from the engine. The second locking nut abuts against the bearing body, and the inner ring of the bearing body is axially pressed by the second locking nut, thereby connecting the bearing assembly to the bushing.

[0024] Optionally, the outer ring of the wave spring washer has a gap with the radial inner wall of the mounting cavity.

[0025] Optionally, the wave spring washer is in a pre-compressed state when it is axially clamped between the end face of the bearing sleeve and the annular stepped surface in the mounting cavity.

[0026] Optionally, the bearing assembly further includes bearing washers disposed on one or both sides of the bearing body and the bearing sleeve along the axial direction.

[0027] Optionally, the bearing washer is at least disposed on the side of the bearing body and bearing sleeve near the wave spring washer and abuts against the wave spring washer.

[0028] Beneficial effects: The present invention has at least one or more of the following advantages:

[0029] 1. Axial tension elastic buffer: The present invention transfers the axial tension that originally acted directly on the bearing and engine to the casing by setting a wave spring washer between the bearing assembly and the casing, and absorbs the impact load by elastic deformation, thereby reducing the peak value of the axial force.

[0030] 2. Reduce bearing load and extend service life: After the axial impact force of the present invention is distributed by the wave spring washer, the axial load of the engine output shaft bearing and the motor bearing is significantly reduced, which helps to reduce wear and extend the service life of bearings and related components.

[0031] 3. Adaptable to complex working conditions: Under conditions of frequent start-stop, drastic load changes, and large fluctuations in axial force, the wave spring washer of this invention can automatically deform according to the actual force, and has a certain self-adaptive ability, making the transmission system run more smoothly and reliably.

[0032] 4. Clear structure and easy assembly: The torque transmission of this invention is achieved through a straight spline hollow shaft and a straight gear coupling. Axial force management is undertaken by the bushing-bearing-wave spring washer-casing link. The two load paths are clearly separated, which is beneficial for processing, assembly and later maintenance. Attached Figure Description

[0033] Figure 1A This is a partial structural schematic diagram of the hybrid power system of the present invention;

[0034] Figure 1B for Figure 1A A magnified view of a portion of the image;

[0035] Figure 2 This is a partial perspective sectional view of the hybrid power system of the present invention;

[0036] Figure 3 This is a partial structural connection diagram of the hybrid power system of the present invention;

[0037] Figure 4 for Figure 3 Exploded view;

[0038] Figure 5 for Figure 4 A sectional view;

[0039] Figures 6A to 6D This is a simulation diagram of the bushing under static stress according to the present invention;

[0040] Figure 7 A cross-sectional view of a connection using a spur gear coupling assembly in a hybrid power system;

[0041] Figure 8 for Figure 7 A magnified view of a portion of the image;

[0042] Figures 9A to 9D This is a multibody dynamics simulation diagram using a spur gear coupling assembly. Detailed Implementation

[0043] The preferred embodiments of the present invention will be described in detail below with reference to the accompanying drawings, so as to better understand the purpose, features and advantages of the present invention. It should be understood that the embodiments shown in the drawings are not intended to limit the scope of the present invention, but are only for illustrating the essential spirit of the technical solution of the present invention.

[0044] In the following description, certain specific details are set forth for the purpose of illustrating various disclosed embodiments in order to provide a thorough understanding of the various disclosed embodiments. However, those skilled in the art will recognize that the embodiments may be practiced without one or more of these specific details. In other instances, well-known apparatuses, structures, and techniques associated with this application may not have been shown or described in detail to avoid unnecessarily obscuring the description of the embodiments.

[0045] Throughout this specification, references to "an embodiment" or "an embodiment" indicate that a particular feature, structure, or characteristic described in connection with the embodiment is included in at least one embodiment. Therefore, the appearance of "in an embodiment" or "an embodiment" in various places throughout the specification does not necessarily refer to the same embodiment. Furthermore, a particular feature, structure, or characteristic may be combined in any manner in one or more embodiments.

[0046] In the following description, in order to clearly demonstrate the structure and operation of the present invention, a number of directional terms will be used. However, terms such as "front", "back", "left", "right", "outside", "inside", "outward", "inward", "up", and "down" should be understood as convenient terms and not as limiting terms.

[0047] The axial direction referred to in this article refers to the axial direction of shafts such as engine output shafts.

[0048] The flexible coupling assembly in this embodiment is used to dissipate the pulling force generated by the engine in a hybrid power system. Specifically, the hybrid power system includes an engine and an output motor driven by the engine to generate electrical energy. The housings of the engine and the output motor are respectively fixedly connected to a casing disposed between them, that is, the casing provides a mounting and fixing function.

[0049] Reference Figures 1A to 5 This invention provides an elastic coupling assembly, which includes a straight-tooth spline hollow shaft 10, a straight-tooth coupling 20, a bearing assembly 30, and a wave spring washer 40.

[0050] The end of the spur-spline hollow shaft 10 closest to the engine is used to axially abut or connect with the bushing 60 fitted over the engine output shaft 50. That is, when the engine output shaft 50 rotates, torque is sequentially transmitted from the engine output shaft 50 to the bushing 60, and then from the bushing 60 to the spur-spline hollow shaft 10, causing the spur-spline hollow shaft 10 to rotate synchronously with the engine output shaft. The inner circle of the end of the spur-spline hollow shaft 10 furthest from the engine has spur-tooth internal splines 11.

[0051] A spur gear coupling 20 has a spur external spline 21 on its outer circumference at the end furthest from the output motor. The spur gear coupling 20 extends from this side into the inner bore of the spur spline hollow shaft 10 at the end furthest from the engine. The spur external spline 21 meshes with the spur internal spline 11, thereby achieving torque transmission between the spur gear coupling 20 and the spur spline hollow shaft 10. The outer surface of the spur gear coupling 20 near the output motor has a first spur tooth 22 for meshing with the output end of the output motor.

[0052] In use, the sleeve 60 fitted over the engine output shaft 50 (e.g., the power turbine output shaft) abuts or connects to the side of the spur spline hollow shaft 10 closest to the engine. The second spur tooth 71 on the output end 70 of the output motor meshes with the first spur tooth 22. During operation, the spur spline hollow shaft 10 transmits torque to the spur coupling 20 via the external spur spline 21 / internal spur spline 11, and then the meshing of the first spur tooth 22 and the second spur tooth 71 transmits the torque to the output motor, achieving coaxial torque transmission and flexible connection between the engine and the output motor.

[0053] Typically, an engine includes an exhaust assembly, a compressor, a starter motor, a diffuser, guide vanes, a combustion chamber, a gas turbine, a power turbine, and an integrated intake shroud. The gas turbine is connected to the compressor via a shaft, and the power turbine output shaft (i.e., the engine output shaft 50) is connected to the output motor via the flexible coupling assembly of this invention. When the engine is operating, the compressor compresses the air, which then enters the diffuser for further compression. The diffuser passes the further compressed gas to the guide vanes, which in turn pass the gas into the combustion chamber. The gas mixes with fuel and ignites, and the combustion of air in the combustion chamber forms high-temperature, high-pressure gas. The high-temperature, high-pressure gas generated by the rotation of the gas turbine drives the power turbine to rotate.

[0054] The torque generated by the power turbine is first transmitted through the power turbine output shaft. A bushing 60 is fitted over the power turbine output shaft, and the two are fixedly connected by a spur spline or an interference fit, so that the bushing 60 rotates synchronously with the power turbine output shaft, thereby transmitting the torque from the power turbine output shaft to the bushing 60. Since the bushing 60 abuts or connects with the spur spline hollow shaft 10, the torque continues to be transmitted to the spur spline hollow shaft 10.

[0055] The internal straight spline 11 on the inner circle of the spur spline hollow shaft 10 meshes with the external straight spline 21 on the outer circle of the spur coupling 20, transmitting torque from the spur spline hollow shaft 10 to the spur coupling 20 in a coaxial state. The first straight tooth 22 on the outer circle of the spur coupling 20 near the output motor meshes with the second straight tooth 71 on the output end 70 of the output motor, further transmitting torque to the output motor shaft, thus realizing the engine's drive or start function for the output motor. The spur spline and spur coupling primarily bear circumferential torque loads and generate virtually no additional axial force, which simplifies axial force management.

[0056] When the output motor operates in reverse as a starter, the torque is transmitted in the reverse direction along the above path, and is transmitted back to the engine output shaft 50, which is the power turbine output shaft, via the spur gear coupling 20, the spur gear spline hollow shaft 10, and the bushing 60, thereby starting the engine.

[0057] During engine start-stop, sudden speed changes, or operating condition switching, the engine output shaft may generate an axial tension along the axis and pointing towards the engine side. This invention uses a wave spring washer 40 to buffer and balance this axial tension. Specifically:

[0058] The bearing assembly 30 is positioned between the radially outer surface of the bushing 60 and the bearing mounting cavity pre-reserved in the radially inner wall of the casing 80. The bearing assembly 30 secures the flexible coupling assembly within the casing 80. The inner ring of the bearing assembly 30 mates with the outer circle of the bushing 60, while the outer ring is pressed into the bearing mounting cavity of the casing 80. An axial shoulder (or step) is formed in the casing 80 within the bearing mounting cavity near the engine side. A wave spring washer 40 is axially clamped between the end face of the outer ring of the bearing assembly 30 and this shoulder, and is in a pre-compressed state.

[0059] When the present invention is used, the entire flexible coupling assembly is supported in the housing 80 by the bearing assembly 30 arranged on the outside of the bushing 60, so that the power turbine output shaft and the output motor shaft maintain good coaxiality and stable torque transmission during operation.

[0060] The axial tensile force is transmitted from the engine output shaft 50 through the bushing 60, bearing assembly 30, wave spring washer 40 to the casing 80.

[0061] The working load and uncompressed thickness of the wave spring washer 40 can be determined according to the actual application scenario. For example, the working load range of the wave spring washer 40 is 0 to 1200 N, and the uncompressed thickness is approximately 4 mm. Its initial compression force can be matched and set according to the axial tension that the engine may generate. When the axial tension is lower than the initial compression force, the bearing assembly 30 basically does not undergo axial displacement, and the shaft system remains rigidly positioned; when the axial tension exceeds this value, the bearing steel sleeve in the bearing assembly 30 moves slightly axially towards the engine side, compressing the wave spring washer 40. The elastic deformation of the wave spring washer 40 absorbs part of the impact energy, and its reaction force is opposite in direction and similar in magnitude to the axial tension, thereby buffering and balancing the axial tension.

[0062] Therefore, in this invention, the axial tension generated by the engine is borne by the wave spring washer 40 and distributed to the whole structure through the housing 80; the torque generated by the engine is transmitted to the output motor through the spur spline and spur coupling and is utilized.

[0063] The spur spline hollow shaft 10 and the spur coupling 20 are engaged by spur teeth, which theoretically does not produce additional axial separation. It mainly bears the torque in the circumferential direction. In other words, since the spur coupling 20 does not transmit additional axial force, the axial load is mainly concentrated in the support link of "shaft sleeve 60-bearing assembly 30-wave spring washer 40-casing 80", which significantly reduces the axial force on the engine and output motor bearings.

[0064] In one embodiment, there is a gap between the outer circle of the wave spring washer 40 and the radial direction of the housing 80, so as to allow the wave spring washer 40 to undergo elastic deformation.

[0065] In one embodiment, the elastic modulus of the wave spring washer 40 is 210.8 N / mm, the working load of the wave spring washer 40 is 1274.9 N, and the pre-compression of the wave spring washer 40 is 2 mm to 3 mm.

[0066] This embodiment describes one design parameter for the wave spring washer 40. Of course, wave spring washers 40 with other design parameters can be selected according to the actual application scenario.

[0067] In one embodiment, the uncompressed thickness of the wave spring washer 40 is 4 mm.

[0068] In one embodiment, the spur gear coupling 20 is provided with a coupling through hole that extends through both sides, and the coupling through hole communicates with the interior of the spur gear spline hollow shaft 10.

[0069] In one embodiment, the outer diameter of one side of the spur gear coupling 20 is larger than the outer diameter of the other side.

[0070] In one embodiment, reference is made to Figure 1B and Figure 5 The spur spline hollow shaft 10 has a hollow shaft step 12 extending towards the shaft center on the side near the engine. The end face of the hollow shaft step 12 near the engine abuts against the bushing 60, and the other end face away from the engine abuts against the first locking nut 13. The first locking nut 13 is used to thread a connection with the engine output shaft 50 that passes through the hollow shaft step 12. The end face of the hollow shaft step 12 near the engine abuts against the bushing 60 through the first locking nut 13.

[0071] Reference Figures 1A to 5 The present invention also provides a hybrid power system, which includes an engine and an output motor, and the engine and the output motor are connected by a flexible coupling assembly provided in the above embodiments of the present invention.

[0072] During connection, the engine's power turbine output shaft is connected to the bushing 60 via a spur spline or interference fit. The bushing 60 abuts against or connects to the spur spline hollow shaft 10 on the side closest to the engine. The output end 70 of the output motor is provided with a second spur tooth 71, which meshes with the first spur tooth 22 of the spur coupling 20.

[0073] In one embodiment, refer to FIG1 and Figure 2 , Figure 5 The spur spline hollow shaft 10 has a hollow shaft step 12 extending towards the shaft center on the side near the engine. The outer surface of the bushing 60 has a platform that mates with the hollow shaft step 12. The platform extends into the side of the spur spline hollow shaft 10 near the engine. The end of the power turbine output shaft away from the engine passes through the hollow shaft step 12 from the side of the spur spline hollow shaft 10 near the engine and is threaded to the first locking nut 13 on the other side of the hollow shaft step 12 away from the engine, so as to achieve a fixed connection with the spur spline hollow shaft 10. The end face of the spur spline hollow shaft 10 near the engine is abutted against the end face of the bushing 60 by the first locking nut 13.

[0074] In this embodiment, the first locking nut 13 and the end face of the bushing platform are positioned on both sides of the hollow shaft step 12, clamping the hollow shaft step 12 between them. This locks the engine output shaft 50, bushing 60 and spur spline hollow shaft 10 in the axial direction and forms a rigid connection in the circumferential direction, allowing the three to rotate together as a whole.

[0075] In one embodiment, reference is made to Figures 1A to 5 The output motor shaft is connected to a motor spline, which serves as the output end 70 of the output motor. The inner circle of the motor spline is provided with a second spur tooth 71.

[0076] In one embodiment, reference is made to Figures 1A to 2The hybrid power system also includes a housing 80, which is disposed between the engine and the output motor. One end of the housing 80 is fixedly connected to the engine housing, and the other end of the housing 80 is fixedly connected to the output motor housing. A flexible coupling assembly is fixed to the housing 80 by a bearing assembly 30 disposed outside the bushing 60.

[0077] The housing 80 is used for mounting and fixing, that is, mounting bracket. In this embodiment, the housing 80 integrates the various components of the hybrid power system together.

[0078] In one embodiment, the housing 80 is provided with a stepped mounting cavity 81 extending axially. The mounting cavity 81 includes an open section for pressing in the bearing sleeve 32 and forms an annular stepped surface in the hole. The annular stepped surface is used to carry the wave spring washer 40 to achieve axial limiting / elastic support.

[0079] Refer to Figure 1 to Figure 5 The bearing assembly 30 includes a bearing body 31 and a bearing sleeve 32. The outer ring of the bearing body 31 is installed in the inner hole of the bearing sleeve 32. The inner ring of the bearing body 31 is fitted onto the bushing 60. The outer circle of the bearing sleeve 32 is pressed into the mounting cavity 81. A wave spring washer 40 abuts between the end face of the bearing sleeve 32 near the engine and the annular stepped surface. A second locking nut 33 is threaded onto the bushing 60 on the other side of the bearing sleeve 32 away from the engine. The second locking nut 33 abuts against the bearing body 31. The inner ring of the bearing body 31 is axially pressed by the second locking nut 33, thereby realizing the connection between the bearing assembly 30 and the bushing 60.

[0080] In this embodiment, the bearing body 31 can be a rolling bearing. The bearing body 31 is fitted onto the outer circle of the bushing 60, which is sleeved outside the engine output shaft 50. The inner ring of the bearing body 31 mates with the bushing 60 and is axially pressed and positioned by the second locking nut 33, so that the bearing assembly 30 rotates together with the bushing 60 and the engine output shaft 50. The outer ring of the bearing body 31 is assembled in the inner hole of the bearing steel sleeve 32, and the two are fixed by an interference fit. The bearing steel sleeve 32 is pressed into the pre-reserved cylindrical mounting cavity inside the housing 80.

[0081] A wave spring washer 40 is arranged between the end face of the bearing sleeve 32 near the engine and the annular stepped surface (axial shoulder) of the housing 80 located in the mounting cavity. The wave spring washer 40 contacts the bearing sleeve 32 and the annular stepped surface of the housing 80 only through its two end faces. Preferably, a gap is left between the outer circle of the wave spring washer 40 and the radial inner wall of the mounting cavity of the housing 80 for axial elastic support of the bearing sleeve 32. The wave spring washer 40 is in a pre-compressed state when it is axially clamped between the end face of the bearing sleeve 32 and the annular stepped surface in the mounting cavity 81.

[0082] In one embodiment, the assembly process of the hybrid power system during implementation is as follows:

[0083] Press the bearing body 31 into the bearing steel sleeve 32 so that the outer ring of the bearing body 31 is fixed with the inner hole of the bearing steel sleeve 32 by interference fit.

[0084] Place the wave spring washer 40 on the annular stepped surface of the mounting cavity of the housing 80;

[0085] The bearing sleeve 32 with the bearing body 31 installed is pressed into the mounting cavity of the casing 80 from the output motor side, so that the end face of the bearing sleeve 32 near the engine side presses against the wave spring washer 40, and the axial limit of the bearing sleeve 32 is achieved by the annular stepped surface (via the wave spring washer 40) in the mounting cavity.

[0086] Insert the bushing 60 into the inner ring of the bearing body 31 from the output motor side, and axially press the inner ring of the bearing body 31 by the second locking nut 33 on the bushing 60, so as to achieve a reliable connection between the bearing assembly 30 and the bushing 60.

[0087] From the engine side, the engine output shaft 50 passes through the bushing 60 and extends into the inner cavity of the straight spline hollow shaft 10, so that the platform end face of the bushing 60 abuts against one side of the hollow shaft step 12 of the straight spline hollow shaft 10. The first locking nut 13 is screwed on the other side of the hollow shaft step 12, thus completing the axial clamping and rigid connection between the engine output shaft 50, the bushing 60 and the straight spline hollow shaft 10.

[0088] Finally, connect one end of the spur gear coupling 20 to the motor spline on the output motor, and the other end to the external spline of the spur gear hollow shaft 10, thus completing the assembly of the entire spring coupling assembly.

[0089] In one embodiment, reference is made to Figure 4 and Figure 5 The bearing assembly 30 also includes a bearing washer 34, which is disposed on one or both sides of the bearing body 31 and the bearing sleeve 32 along the axial direction. Preferably, the bearing washer 34 is disposed at least on the side of the bearing body 31 and the bearing sleeve 32 near the wave spring washer 40 and abuts against the wave spring washer 40.

[0090] The bearing washer 34 is a flat washer located on one side of the bearing assembly 30 near the wave spring washer 40 and / or the second locking nut 33. It serves as an auxiliary force-bearing component or a separating element and is an optional part. The bearing washer 34 serves the following functions:

[0091] (1) Force transmission surface / pressure plate: The axial force transmitted by the wave spring washer 40 or the second locking nut 33 is evenly transmitted to the outer ring of the bearing body 31 (or the end face of the bearing steel sleeve 32) to avoid point contact and local indentation.

[0092] (2) Protect the spring and bearing end face: The edge of the wave spring washer 40 is relatively sharp and directly presses against the outer ring of the bearing body 31 or the end face of the bearing steel sleeve 32. Long-term reciprocating compression will wear out the end face; adding the bearing washer 34 is equivalent to making a "smooth force-bearing surface".

[0093] (3) Fine-tuning axial position / clearance: Selecting different bearing washer 34 washer thicknesses can be used to fine-tune the preload and installation dimensions, so that the working position between the bearing assembly 30 and the wave spring washer 40 is more suitable.

[0094] Reference Figure 7 and Figure 8 A spur gear coupling assembly is provided for use in a hybrid power system as a comparative example. The engine and the output motor are connected by the spur gear coupling assembly, which includes a spur gear spline hollow shaft 91, a spur gear coupling 92, a spur gear bushing 93, and a spur gear bearing assembly 94.

[0095] One side of the spur-spline hollow shaft 91 abuts against or connects to the spur-spline sleeve 93. The connection between the spur-spline hollow shaft 91 and the spur-spline sleeve 93 can be the same as that between the spur-spline hollow shaft 10 and the sleeve 60 in the spring coupling assembly of the present invention. The spur-spline sleeve 93 is sleeved on the outside of the engine output shaft 50, and the spur-spline sleeve 93 and the engine output shaft 50 are connected by a spur-spline or interference fit.

[0096] One side of the spur gear coupling 92 extends into the other side of the spur gear hollow shaft 91 and is connected to the spur gear hollow shaft 91 with straight teeth. The other side of the spur gear coupling 92 is connected to the output end 70 of the output motor with straight teeth.

[0097] The spur gear bearing assembly 94 is disposed outside the spur gear sleeve 93, and the spur gear coupling assembly is fixed inside the housing 80 by the spur gear bearing assembly 94. The spur gear bearing assembly 94 adopts the prior art.

[0098] Similar to the spring coupling assembly of this invention, the spur gear coupling assembly in the comparative example uses spur gear meshing, making the transmission structure simpler, easier to process and assemble, and effectively reducing manufacturing costs. Simultaneously, this design provides a clear force transmission path during operation, facilitating mechanical analysis and troubleshooting of the system. However, unlike the spring coupling assembly of this invention, the spur gear bearing assembly 94 in the comparative example does not include the wave spring washer 40. Due to the use of spur gear meshing, the engine alone bears the axial tension, while the output motor and casing do not bear axial force. Under normal operating conditions, the spur gear coupling assembly can stably transmit power, meeting basic transmission requirements. However, because the engine alone bears the axial tension, after long-term operation, engine-related components may experience a certain degree of wear, requiring regular maintenance and inspection. Therefore, the spur gear coupling assembly is suitable for applications where transmission accuracy requirements are not particularly high, operating conditions are relatively stable, and axial force variations are small.

[0099] After applying the spring coupling assembly of the present invention and the spur gear coupling assembly of the comparative example to the same hybrid power system, the parameters were compared, and the comparison results are shown in the table below:

[0100]

[0101] As can be seen, by using the spring coupling assembly, the maximum stress in the casing (80 MPa) is lower than the material's yield strength of 250 MPa, meeting the design requirements. The spring coupling assembly not only offers high transmission efficiency but also effectively balances axial forces, thereby extending the bearing's service life.

[0102] Reference Figures 9A to 9D This is a multibody dynamics simulation diagram of a proportional spur gear coupling assembly, in which... Figure 9A This is a diagram showing the stress and stress distribution. Figure 9B This is a diagram illustrating the strain. Figure 9C This is a diagram illustrating the displacement. Figure 9D This is a schematic diagram of the mesh quality. Because the spur gear coupling assembly uses spur gear meshing, the peak impact force of the gear meshing reaches 1200N, requiring optimization of the tooth surface profile. This demonstrates that the spur gear coupling assembly is relatively weak in axial force dissipation, affecting its service life.

[0103] Reference Figures 6A to 6D This is a simulation diagram of the bushing 60 in the spring coupling assembly of the present invention under static stress. Figure 6A This is a diagram showing the stress and stress distribution. Figure 6B This is a diagram illustrating the strain. Figure 6C This is a diagram illustrating the displacement. Figure 6D This is a schematic diagram of the grid quality.

[0104] Depend on Figures 6A to 6DIt can be seen that the maximum stress on bushing 60 is 3.558 MPa, the yield strength is 206.8 MPa, and the safety factor is 203.2, which meets the design requirements.

[0105] The preferred embodiments of the present invention have been described in detail above. However, it should be understood that after reading the above teachings, those skilled in the art can make various alterations or modifications to the present invention. These equivalent forms also fall within the scope defined by the appended claims.

Claims

1. A flexible coupling assembly, characterized in that, The flexible coupling assembly includes: A spur-tooth hollow shaft, wherein the side of the spur-tooth hollow shaft closer to the engine is used to abut or connect with a bushing fitted around the engine output shaft of the engine, and the inner circle of the other side of the spur-tooth hollow shaft away from the engine has a spur-tooth internal spline; A spur gear coupling has a spur external spline on its outer circumference away from the output motor. The spur gear coupling extends from the side away from the output motor into the interior of the spur spline hollow shaft on the other side away from the engine. The spur external spline meshes with the spur internal spline. The outer surface of the spur gear coupling near the output motor has a first spur tooth for meshing with the output end of the output motor. A bearing assembly is provided, which is disposed between the radial outer surface of the bushing and the radial inner wall of the casing, and fixes the flexible coupling assembly inside the casing. The casing is disposed between the engine and the output motor. One end of the casing is fixedly connected to the housing of the engine, and the other end of the casing is fixedly connected to the housing of the output motor. A wave spring washer is located between the axial side of the bearing assembly and the axial inner wall of the casing.

2. The flexible coupling assembly as described in claim 1, characterized in that, There is a gap between the outer circle of the wave spring washer and the radial direction of the casing; And / or, the elastic modulus of the wave spring washer is 210.8 N / mm, the working load of the wave spring washer is 1274.9 N, and the pre-compression of the wave spring washer is 2 mm to 3 mm; And / or, the uncompressed thickness of the wave spring washer is 4 mm.

3. The flexible coupling assembly as described in claim 1, characterized in that, The spur gear coupling is provided with a coupling through hole that extends through both sides, and the coupling through hole communicates with the interior of the spur gear spline hollow shaft.

4. The flexible coupling assembly as described in claim 1, characterized in that, The spur-tooth spline hollow shaft has a hollow shaft step extending towards the shaft center on the side closest to the engine. The end face of the hollow shaft step closest to the engine abuts against the bushing, and the end face furthest from the engine abuts against the first locking nut. The first locking nut is used to thread a connection with the engine output shaft that passes through the hollow shaft step. The end face of the hollow shaft step closest to the engine abuts against the bushing through the first locking nut.

5. A hybrid power system, the hybrid power system comprising an engine and an output motor, characterized in that, The engine and the output motor are connected by a flexible coupling assembly as described in any one of claims 1 to 4; The power turbine output shaft of the engine is connected to a bushing via a spur spline or interference fit, and the bushing abuts against or is connected to the side of the spur spline hollow shaft near the engine. The output end of the output motor is provided with a second straight tooth, which meshes with the first straight tooth of the straight tooth coupling.

6. The hybrid power system as described in claim 5, characterized in that, The spur-spline hollow shaft has a hollow shaft step extending towards the shaft center on the side closest to the engine. The outer surface of one side of the bushing has a platform that mates with the hollow shaft step. The platform extends into the side of the spur-spline hollow shaft closest to the engine. The end of the power turbine output shaft away from the engine passes through the hollow shaft step from the side of the spur-spline hollow shaft closest to the engine and is threaded to a first locking nut on the other side of the hollow shaft step away from the engine, thereby achieving a fixed connection with the spur-spline hollow shaft. The first locking nut abuts the end face of the spur-spline hollow shaft closest to the engine against the end face of the bushing.

7. The hybrid power system as described in claim 5, characterized in that, The output motor shaft is connected to a motor spline, and the inner circle of the motor spline is provided with the second straight tooth.

8. The hybrid power system as described in any one of claims 5 to 7, characterized in that, The hybrid power system also includes a housing disposed between the engine and the output motor, one end of the housing being fixedly connected to the housing of the engine, and the other end of the housing being fixedly connected to the housing of the output motor; The flexible coupling assembly is fixed to the housing by a bearing assembly disposed outside the bushing.

9. The hybrid power system as described in claim 8, characterized in that, The casing is provided with a stepped mounting cavity extending along the axial direction. The mounting cavity includes an open hole section for pressing in the bearing steel sleeve, and an annular stepped surface is formed in the hole. The bearing assembly includes a bearing body and a bearing sleeve. The outer ring of the bearing body is installed in the inner hole of the bearing sleeve, and the inner ring of the bearing body is fitted onto the bushing. The outer circle of the bearing sleeve is pressed into the mounting cavity. A wave spring washer abuts between the end face of the bearing sleeve near the engine and the annular stepped surface. A second locking nut is threaded onto the bushing on the other side of the bearing sleeve away from the engine. The second locking nut abuts against the bearing body, and the inner ring of the bearing body is axially pressed by the second locking nut, thereby connecting the bearing assembly to the bushing.

10. The hybrid power system as claimed in claim 9, characterized in that, The outer ring of the wave spring washer has a gap with the radial inner wall of the mounting cavity; And / or, the wave spring washer is in a pre-compressed state when it is axially clamped between the end face of the bearing steel sleeve and the annular stepped surface in the mounting cavity; And / or, the bearing assembly further includes a bearing washer disposed on one or both sides of the bearing body and the bearing sleeve along the axial direction; Preferably, the bearing washer is disposed at least on the side of the bearing body and bearing sleeve near the wave spring washer and abuts against the wave spring washer.

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