Power dividing gear uniform load adjusting transmission device and uniform load adjusting measure

Abstract

The invention discloses a power dividing gear uniform-load adjusting transmission device and a uniform-load adjusting measure. The power dividing gear uniform-load adjusting transmission device comprises an output gear, an input gear and a plurality of power dividing transmission chains. Each power dividing transmission chain comprises a transmission shaft set used for conducting circumferential and axial error compensation through flexible deformation, a dividing gear, a parallel operation gear and an adjusting pad. The transmission shaft set extends in the power transmission direction, the parallel operation gear and the flow dividing gear are sequentially, detachably and fixedly arranged on the transmission shaft set front and back in the axial direction of the transmission shaft set, the parallel operation gear is further externally meshed with the output gear, and the flow dividing gear is externally meshed with the input gear. The adjusting pad is arranged on the outer circle of the transmission shaft set and clamped between the rear end of the flow dividing gear and the rear end of the transmission shaft set in the axial direction. According to the power dividing gear transmission device, the axial distance between the center face of the dividing gear and the center face of the parallel operation gear on each transmission chain is consistent and adjustable, so that the uniform load performance of a gear train is improved, and the bearing capacity, reliability and service life of the power dividing gear transmission device are guaranteed.

Description

Technical Field

[0001] This invention relates to the field of power split gear transmission technology, and in particular, to a power split gear load-sharing adjustment transmission device. Furthermore, this invention also relates to a load-sharing adjustment measure utilizing the aforementioned power split gear load-sharing adjustment transmission device. Background Technology

[0002] As the power levels of aviation and other industrial power sources continue to increase, the loads transmitted by their gear transmission devices are becoming increasingly larger. Single-path gear transmissions can no longer meet the demands of high-power systems, leading to the increasingly widespread application of power-splitting gear transmission devices. In power-splitting gear transmission devices, there is always a certain amount of backlash in the gear meshing. Furthermore, due to unavoidable manufacturing errors, installation errors, and errors caused by the elastic deformation of components, the load transmitted in each branch is always unbalanced, which can severely reduce the gear's load-bearing capacity. To achieve load equalization in each branch, elastic elements are typically installed in the branches. The deformation of these elastic elements under load compensates for various errors, thus balancing the load transmitted in each branch.

[0003] Existing document - CN204477198U, transmission system load-sharing structure, as attached. Figure 1 As shown, the first herringbone gear 11 and the second herringbone gear 14 are connected by an elastic long shaft 12 and a spline connecting sleeve 13. The torsional deformation of the elastic long shaft 12 is used to overcome the error generated during the transmission process and to achieve uniform distribution of loads in the system.

[0004] The main disadvantages of the load-sharing structure of the transmission system disclosed in the existing document are as follows: 1) After the first herringbone gear 11 and the second herringbone gear 14 are connected by the elastic long shaft 12 and the spline connecting sleeve 13, the axial distance between the centers of the first herringbone gear 11 and the second herringbone gear 14 is fixed and their relative axial positions are not adjustable. 2) Due to errors, the axial distance between the centers of the first herringbone gear 11 and the second herringbone gear 14 on different branches will be different. When the herringbone gears are modified with asymmetrical tooth profiles, the actual axial distance between the centers of the first herringbone gear 11 and the second herringbone gear 14 will change further. When meshing with the corresponding herringbone gears, a problem may arise where the herringbone gear on one branch engages while the herringbone gear on another branch may not engage. This situation will cause the branch that engages first to bear additional loads, thus causing an imbalance in the loads on each branch. 3) The elastic long shaft 12 used can only compensate for the load imbalance caused by various circumferential errors through torsional deformation, but cannot compensate for the load imbalance caused by the axial distance deviation mentioned in points 1) and 2) above. Summary of the Invention

[0005] This invention provides a power-split gear load-sharing adjustment transmission device and load-sharing adjustment measures to solve the technical problems of fixed axial distance, non-adjustable axial relative position, and unbalanced load of each branch in the existing load-sharing structure of the transmission system.

[0006] The technical solution adopted in this invention is as follows: A power-splitting gear load-sharing adjustment transmission device includes: an output gear and an input gear arranged sequentially and at intervals, and multiple power-splitting transmission chains arranged circumferentially between the output gear and the input gear for power-splitting transmission from the input gear to the output gear; each power-splitting transmission chain includes a transmission shaft assembly for circumferential and axial error compensation through flexible deformation, a power-splitting gear, a parallel gear for parallel power transmission, and an adjusting shim for adjusting the axial distance between the power-splitting gear and the parallel gear; the transmission shaft assembly extends along the power transmission direction, and the parallel gear and the power-splitting gear are detachably fixedly mounted sequentially and sequentially on the outer circle of the transmission shaft assembly along the axial direction, with the parallel gear also meshing with the output gear and the power-splitting gear meshing with the input gear; the adjusting shim is mounted on the outer circle of the transmission shaft assembly and is axially clamped between the rear end of the power-splitting gear and the rear end of the transmission shaft assembly.

[0007] Furthermore, the drive shaft assembly includes an elastic shaft extending along the power transmission direction and a transfer plate fixedly mounted on the outer circle of the rear end of the elastic shaft; a parallel gear is detachably fixedly mounted on the outer circle of the front end of the elastic shaft; a split gear is detachably fixedly mounted on the outer circle of the transfer plate; and an adjusting shim is mounted on the outer circle of the transfer plate and is axially clamped between the rear end of the split gear and the first shoulder protruding from the rear end of the transfer plate.

[0008] Furthermore, the elastic shaft includes a hollow thin-walled elastic shaft body, a first flexible thin-spoke plate connected to the rear end of the elastic shaft body, and a first flange connected to the outer ring of the first flexible thin-spoke plate; the adapter plate includes an adapter plate body fitted onto the outer circle of the rear end of the elastic shaft body, a second flexible thin-spoke plate connected to the rear end of the adapter plate body, and a second flange connected to the outer ring of the second flexible thin-spoke plate, wherein the second flange and the first flange are locked and fixed by multiple sets of bolts and self-locking nuts arranged sequentially and spaced apart along the circumference.

[0009] Furthermore, the outer circle at the front end of the adapter plate is provided with a first external thread; the inner shaft hole of the split gear has a first protruding shoulder; the split gear and the adapter plate are slidably connected by a first spline structure; and the outer circle at the front end of the adapter plate is also provided with a first clamping nut to press against the first shoulder, thereby pressing the adjusting pad between the rear end of the split gear and the first shoulder.

[0010] Furthermore, the outer circles of the front and rear ends of the elastic shaft are provided with a second external thread and a second protruding shoulder in sequence; the inner shaft hole of the parallel gear has a second protruding shoulder, the parallel gear and the elastic shaft are slidably connected by a second spline structure, and a second clamping nut is also installed on the outer circle of the front end of the elastic shaft to press against the front end of the parallel gear, thereby causing the second shoulder of the parallel gear to abut against the second shoulder of the elastic shaft for axial limitation.

[0011] Furthermore, the output gear, parallel gear, split gear, and input gear are all herringbone gears; cylindrical roller bearings are installed at both ends of the input gear, both ends of the split gear, both ends of the parallel gear, and the rear end of the output gear, and ball bearings are installed at the front end of the parallel gear.

[0012] According to another aspect of the present invention, a load-sharing adjustment measure for a power-splitting gear transmission is also provided, employing a power-splitting gear load-sharing adjustment transmission as described above, wherein: i Indices: subscripts, i = 1 or 2 ... or n, where 1 represents the first power shunt transmission chain, 2 represents the second power shunt transmission chain, and n represents the nth power shunt transmission chain; a i Indicates: the axial distance from the center face of the parallel gear to the rear end face of the second shoulder of the parallel gear; b i Indicates the axial distance from the center surface of the splitter gear to the center surface of the parallel gear; c i Indicates: the axial distance from the center face of the splitter gear to the rear bearing mounting shoulder; d i Indicates the width of the inner ring of the rear bearing of the splitter gear; e i Indicates: Adjust the thickness of the shim; f i Indicates: the axial distance from the front end face of the first shoulder of the adapter plate to the rear end face of its second flange; g i Indicates: the axial distance from the front end face of the first flange of the elastic shaft to the front end face of its second shoulder; the axial distance between the center faces of the split gear and the parallel gear. b i Calculate using the following formula: The load-sharing adjustment measures for power split gear transmission devices include: replacing the adjusting shims or grinding the thickness of the adjusting shims.

[0013] Furthermore, the load-sharing adjustment measures for the power split gear transmission device also include: setting the structure and thickness of the first flexible thin spoke and the second flexible thin spoke so that they can undergo axial deformation for compensation after being loaded.

[0014] Furthermore, the load-sharing adjustment measures for the power split gear transmission device also include: controlling the manufacturing error of the herringbone gear to control the symmetry of the left and right helical teeth of the herringbone gear.

[0015] Furthermore, the load-sharing adjustment measures for the power split gear transmission device also include: when calculating bi, the influence of the herringbone gear tooth profile modification is also considered, and the actual center surface position of the herringbone gear is accurately calculated.

[0016] The present invention has the following beneficial effects: In the transmission device of the present invention, the transmission shaft assembly in each power splitting transmission chain can compensate for circumferential and axial errors through flexible deformation. When compensating for circumferential errors, it can compensate for the load imbalance caused by various circumferential errors. When compensating for axial errors, it can compensate for the axial distance between the center plane of the splitting gear and the center plane of the parallel gear on each power splitting transmission chain, thereby solving the load imbalance problem caused by the difference in the axial distance between the center planes of the splitting gear and the parallel gear on each transmission chain. On the other hand, the transmission device of the present invention also includes an adjusting shim, which is installed on the outer circle of the transmission shaft assembly and is axially clamped between the rear end of the splitting gear and the rear end of the transmission shaft assembly. Thus, by replacing the adjusting shim with an adjusting shim of different thickness or grinding the thickness of the existing adjusting shim, the axial distance between the center plane of the splitting gear and the center plane of the parallel gear on each transmission chain can be kept consistent and the axial distance can be adjusted, thereby improving the load sharing performance of the gear system, ensuring the load-bearing capacity, reliability and life of the power splitting gear transmission device, making the load on each transmission chain balanced, and solving the load imbalance problem caused by the difference in the axial distance between the center planes of the splitting gear and the parallel gear on each transmission chain.

[0017] In addition to the objectives, features, and advantages described above, the present invention has other objectives, features, and advantages. The invention will now be described in further detail with reference to the figures. Attached Figure Description

[0018] The accompanying drawings, which form part of this application, are used to provide a further understanding of the invention. The illustrative embodiments of the invention and their descriptions are used to explain the invention and do not constitute an undue limitation of the invention. In the drawings: Figure 1 This is a schematic diagram of the load-sharing structure of the transmission system in the existing documents; Figure 2 This is an isometric view of the power splitting gear load-sharing adjustment transmission device according to a preferred embodiment of the present invention; Figure 3 This is a front view of the power splitting gear load-sharing adjustment transmission device according to a preferred embodiment of the present invention; Figure 4 yes Figure 3 MM-directed sectional view; Figure 5 yes Figure 4 Schematic diagram for calculating the axial distance between the center plane of the middle split gear and the center plane of the parallel gear; Figure 6 This is a normal sectional view of the pitch circle position of the herringbone gear tooth surface (without tooth profile modification). Figure 7 This is a normal sectional view of the pitch circle position of the herringbone gear tooth surface (with symmetrical tooth profile modification). Figure 8 This is a normal sectional view of the pitch circle position of the herringbone gear tooth surface (with asymmetric tooth profile modification).

[0019] Legend: 11. First herringbone gear; 12. Flexible long shaft; 13. Spline connecting sleeve; 14. Second herringbone gear; 2. Output gear; 3. Input gear; 4. Power shunt transmission chain; 41. Elastic shaft; 411. First flexible thin spoke; 412. Second shoulder; 42. Adapter plate; 421. Second flexible thin spoke plate; 422. First shoulder; 43. Bolt; 44. Self-locking nut; 45. Flow divider gear; 451. First shoulder; 46. ​​Parallel gear; 461. Second shoulder; 47. Adjusting shims; 48. First spline structure; 49. First clamping nut; 51. Second spline structure; 52. Second clamping nut; 53. Cylindrical roller bearing; 54. Ball bearing. Detailed Implementation

[0020] The embodiments of the present invention will be described in detail below with reference to the accompanying drawings. However, the present invention can be implemented in many different ways as defined and covered below. Examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and should not be construed as limiting the present invention.

[0021] Those skilled in the art will understand that, unless specifically stated otherwise, the term "comprising" as used in this specification means the presence of the stated features, integers, steps, operations, components, and / or components, but does not exclude the presence or addition of one or more other features, integers, steps, operations, components, and / or combinations thereof. It should be understood that when we say a component is "connected" to another component, it can be directly connected to the other component or connected via an intermediate component. The term "and / or" as used herein includes all or any unit and all combinations of one or more associated listed items. The terms "first" and "second," etc., in this specification and claims are used to distinguish different objects, not to describe a particular order.

[0022] Reference Figure 2-3 A preferred embodiment of the present invention provides a power-splitting gear load-sharing adjustment transmission device, comprising: an output gear 2 and an input gear 3 arranged sequentially and at intervals, and multiple power-splitting transmission chains 4 arranged circumferentially between the output gear 2 and the input gear 3 for power-splitting transmission from the input gear 3 to the output gear 2. Each power-splitting transmission chain 4 includes a transmission shaft assembly for circumferential and axial error compensation through flexible deformation, a power-splitting gear 45, a parallel gear 46 for parallel power transmission, and an adjusting shim 47 for adjusting the axial distance between the power-splitting gear 45 and the parallel gear 46. The transmission shaft assembly extends along the power transmission direction, and the parallel gear 46 and the power-splitting gear 45 are detachably fixed to the outer circle of the transmission shaft assembly sequentially and sequentially along the axial direction of the transmission shaft assembly. The parallel gear 46 also meshes with the output gear 2 for external transmission, and the power-splitting gear 45 meshes with the input gear 3 for external transmission. The adjusting shim 47 is installed on the outer circle of the drive shaft assembly and is axially clamped between the rear end of the split gear 45 and the rear end of the drive shaft assembly.

[0023] In view of the power splitting gear transmission device using herringbone gear in the prior art, a power splitting gear load-sharing adjustment transmission device is provided. During operation, the input gear 3 simultaneously meshes with the splitting gears 45 in multiple power splitting transmission chains 4 to split and transmit power to each power splitting transmission chain 4. The power in each power splitting transmission chain 4 is then transmitted to the parallel gears 46 through the transmission shaft assembly. The parallel gears 46 of each power splitting transmission chain 4 then mesh with the output gear 2, so that the parallel gears 46 further parallel the power to the output gear 2, and finally the output gear 2 outputs the power.

[0024] In the transmission device of the present invention, the transmission shaft assembly in each power splitting transmission chain 4 can compensate for circumferential and axial errors through flexible deformation. When compensating for circumferential errors, it can compensate for the load imbalance caused by various circumferential errors. When compensating for axial errors, it can compensate for the axial distance between the center plane of the splitting gear 45 and the center plane of the parallel gear 46 on each power splitting transmission chain 4, thereby solving the problem of load imbalance caused by the difference in the axial distance between the center planes of the splitting gear 45 and the parallel gear 46 on each transmission chain. On the other hand, the transmission device of the present invention also includes an adjusting shim 47, and the adjusting shim 47 is installed on the transmission shaft assembly. On the outer circle, and axially clamped between the rear end of the split gear 45 and the rear end of the drive shaft assembly, the axial distance between the center plane of the split gear 45 and the center plane of the parallel gear 46 on each transmission chain can be kept consistent by replacing the adjusting shims 47 of different thicknesses or grinding the thickness of the existing adjusting shims 47. The axial distance is adjustable, thereby improving the load sharing performance of the gear system, ensuring the load-bearing capacity, reliability and life of the power split gear transmission device, making the load on each transmission chain balanced, and solving the problem of load imbalance caused by the difference in the axial distance between the center planes of the split gear 45 and the parallel gear 46 on each transmission chain.

[0025] Optionally, such as Figure 4 As shown, the drive shaft assembly includes an elastic shaft 41 extending along the power transmission direction and a transfer plate 42 fixedly mounted on the outer circumference of the rear end of the elastic shaft 41. A parallel gear 46 is detachably fixedly mounted on the outer circumference of the front end of the elastic shaft 41. A splitter gear 45 is detachably fixedly mounted on the outer circumference of the transfer plate 42. An adjusting shim 47 is mounted on the outer circumference of the transfer plate 42 and axially clamped between the rear end of the splitter gear 45 and the first shoulder 422 protruding from the rear end of the transfer plate 42.

[0026] In this optional solution, such as Figure 4As shown, the elastic shaft 41 includes a hollow, thin-walled elastic shaft body, a first flexible thin-walled plate 411 connected to the rear end of the elastic shaft body, and a first flange connected to the outer ring of the first flexible thin-walled plate 411. In this optional embodiment, the hollow, thin-walled design of the elastic shaft body allows for compensation of load imbalances caused by various circumferential errors through torsional deformation. The adapter plate 42 includes an adapter plate body fitted onto the outer circumference of the rear end of the elastic shaft body, a second flexible thin-walled plate 421 connected to the rear end of the adapter plate body, and a second flange connected to the outer ring of the second flexible thin-walled plate 421. The second flange and the first flange are locked together by multiple sets of bolts 43 and self-locking nuts 44 arranged circumferentially at intervals. In this optional solution, the rear ends of both the adapter plate 42 and the elastic shaft 41 adopt a flexible thin-spread plate structure. The axial deformation generated by the flexible thin-spread plate under load compensates for the difference in the axial distance between the center planes of the split gear 45 and the parallel gear 46 on the corresponding transmission chain, thereby solving the problem of load imbalance caused by the difference in the axial distance between the center planes of the split gear 45 and the parallel gear 46 on each transmission chain.

[0027] In this optional solution, such as Figure 4 As shown, the outer circumferences of the front and rear ends of the adapter plate 42 are provided with a first external thread and a first protruding shoulder 422 in sequence. The inner shaft hole of the split gear 45 has a first protruding shoulder 451. The split gear 45 and the adapter plate 42 are slidably connected by a first spline structure 48. The outer circumference of the front end of the adapter plate 42 is also provided with a first clamping nut 49 to press against the first shoulder 451, thereby pressing the adjusting shim 47 between the rear end of the split gear 45 and the first shoulder 422.

[0028] In this optional solution, such as Figure 4 As shown, the outer circumferences of the front and rear ends of the elastic shaft 41 are sequentially provided with a second external thread and a protruding second shoulder 412. The inner shaft hole of the parallel gear 46 has a protruding second shoulder 461. The parallel gear 46 and the elastic shaft 41 are slidably connected by a second spline structure 51. A second clamping nut 52 is also installed on the outer circumference of the front end of the elastic shaft 41 to press against the front end of the parallel gear 46, thereby causing the second shoulder 461 of the parallel gear 46 to abut against the second shoulder 412 of the elastic shaft 41 for axial limitation.

[0029] In this optional solution, such as Figure 4As shown, the output gear 2, parallel gear 46, split gear 45, and input gear 3 are all herringbone gears. A herringbone gear can essentially be considered as two helical gears with equal helix angles and opposite directions of rotation connected in parallel. During operation, a pair of meshing herringbone gears can generate a self-balancing axial force through their symmetrical helical gear structure, thus enabling the herringbone gears to automatically align their center position. Cylindrical roller bearings 53 are installed at both ends of the input gear 3, both ends of the split gear 45, both ends of the parallel gear 46, and the rear end of the output gear 2. A ball bearing 54 is installed at the front end of the parallel gear 46. The axial positioning of each gear in the transmission device of this invention is as follows: Axial positioning of output gear 2: Axial positioning is achieved through ball bearing 54.

[0030] Axial positioning of parallel gear 46: During the meshing process of the herringbone gears, the center surface of parallel gear 46 and the center surface of output gear 2 are automatically aligned.

[0031] Axial positioning of the split gear 45: The split gear 45 and the parallel gear 46 are fixedly connected by the adapter plate 42, the elastic shaft 41, etc., and its axial position is determined by the parallel gear 46.

[0032] Axial positioning of input gear 3: During the meshing process of the herringbone gear, the center surface of input gear 3 and the center surface of the split gear 45 are automatically aligned and centered.

[0033] In this invention, the specific power transmission method is as follows: Input gear 3 meshes with the split gear 45 of the multi-branch transmission chain to split and transmit power. The split gear 45 transmits power to the adapter plate 42 through the first spline structure 48. The adapter plate 42 and the split gear 45 are fixed by the first clamping nut 49. An adjusting shim 47 is provided between the adapter plate 42 and the split gear 45. Bolts 43 and self-locking nuts 44 are used to connect the adapter plate 42 and the elastic shaft 41. The rear ends of both the adapter plate 42 and the elastic shaft 41 adopt a flange structure with flexible thin spokes. After the power is transmitted to the front end of the elastic shaft 41, it is transmitted to the parallel gear 46 through the second spline structure 51. The parallel gear 46 and the elastic shaft 41 are fixed by the second clamping nut 52, and the second shoulder 412 on the elastic shaft 41 and the second shoulder 461 in the parallel gear 46 are axially engaged. The parallel gears 46 of each branch transmission chain mesh with the output gear 2 simultaneously to parallelize the power, which is finally output by the output gear 2.

[0034] like Figure 5 As shown, a preferred embodiment of the present invention also provides a load-sharing adjustment measure for a power-splitting gear transmission device, employing the power-splitting gear load-sharing adjustment transmission device as described above, wherein: iIndicates: subscript, i=1 or 2... or n, where 1 represents the first power shunt transmission chain 4, 2 represents the second power shunt transmission chain 4, and n represents the nth power shunt transmission chain 4.

[0035] A i Indicates the axial distance from the center surface of the parallel gear 46 to the rear end face of the second shoulder 461 of the parallel gear 46.

[0036] b i Indicates the axial distance from the center surface of the split gear 45 to the center surface of the parallel gear 46.

[0037] c i Indicates the axial distance from the center face of the split gear 45 to the shoulder of the rear bearing mounting shaft.

[0038] d i Indicates the width of the inner ring of the rear bearing of the 45th split gear.

[0039] e i Indicates: Adjust the thickness of pad 47.

[0040] f i Indicates the axial distance from the front face of the first shoulder 422 of the adapter plate 42 to the rear face of its second flange.

[0041] g i Indicates the axial distance from the front end face of the first flange of the elastic shaft 41 to the front end face of its second shoulder 412.

[0042] Axial distance between the center plane of the splitter gear 45 and the center plane of the parallel gear 46 b i Calculate using the following formula: .

[0043] The load-sharing adjustment measures for the power split gear transmission device include: replacing the adjusting shim 47, or grinding the thickness of the adjusting shim 47.

[0044] As stated above, after the axial position of the output gear 2 is fixed, the center planes of the parallel gears 46 and the output gear 2 of each branch transmission chain automatically align during operation. Since the shunt gear 45 and the parallel gear 46 are fixedly connected, the axial position of the shunt gear 45 on each branch transmission chain is also fixed. Due to unavoidable manufacturing and installation errors, the axial distance between the center planes of the shunt gear 45 and the parallel gear 46 on each branch transmission chain is not the same, meaning the axial position of the shunt gear 45 on each branch is different. When the shunt gear 45 of each branch meshes with the input gear 3 simultaneously, the different axial positions of the shunt gear 45 will cause one branch's shunt gear 45 to engage first, while the shunt gears 45 on the other branches will not engage. This situation will cause the branch that engages first to bear additional load, leading to an unbalanced load distribution among the branches. To ensure the load-sharing performance of the gear train, while using the torsional deformation of the elastic shaft 41 to compensate for the load imbalance caused by various circumferential errors, corresponding measures should also be taken to ensure the consistency of the axial distance between the center planes of the split gears 45 and the parallel gears 46 on each branch. Therefore, this invention provides a load-sharing adjustment measure for a power split gear transmission device, which includes replacing the adjusting shim 47 or grinding the thickness of the adjusting shim 47. By grinding the thickness of the adjusting shim 47... e i Alternatively, replacing the shims with new, appropriately thicker shims (47) can ensure the axial distance on each branch. b i Consistency; generally, it can guarantee the axial distance on each branch of the transmission chain. b i The difference is within ±0.01 mm, thereby improving the load sharing performance of the gear train, ensuring the load-bearing capacity, reliability and life of the power split gear transmission device, and solving the problem of load imbalance caused by the difference in the axial distance between the center planes of the split gear 45 and the parallel gear 46 on each transmission chain.

[0045] Optionally, the load-sharing adjustment measures for the power split gear transmission device also include: setting the structure and thickness of the first flexible thin spoke 411 and the second flexible thin spoke 421 so that they can undergo axial deformation for compensation after being loaded. In this configuration, the elastic shaft 41 adopts a thin-walled hollow structure, and the first flexible thin spoke 411 is set at the rear end. While compensating for load imbalances caused by various circumferential errors through torsional deformation, it can also compensate for load imbalances caused by the difference in axial distance between the center planes of the split gear 45 and the parallel gear 46 on each branch through axial deformation together with the second flexible thin spoke 421 on the adapter plate 42. In actual design, the spoke thickness can generally be (0.4~1) mm, thereby compensating for the axial distance on each branch transmission chain through the axial deformation generated by the flexible thin spoke after being loaded. b i The differences.

[0046] Optionally, a normal sectional view of the pitch circle position of the herringbone gear tooth surface without tooth profile modification is attached. Figure 6 As shown, ideally, the left and right helical teeth of a herringbone gear are perfectly symmetrical, and the plane where their extended intersection point lies is the ideal center plane of the gear. In reality, due to various manufacturing errors, the left and right helical teeth are not perfectly symmetrical, which causes their extended intersection point to deviate from the ideal center plane. Therefore, in the adjustment method of this invention, the load-sharing adjustment measures for the power-splitting gear transmission device further include: controlling the manufacturing error of the herringbone gear to control the symmetry of the left and right helical teeth, thereby reducing the offset of the actual center plane of the gear. Generally, it can be specified that the extended intersection point of the left and right helical teeth is within ±0.01 mm of the ideal center plane.

[0047] Optionally, when the left and right helical teeth of a herringbone gear have undergone symmetrical tooth profile modification due to some factors, the normal sectional view of its pitch circle position is shown in the attached figure. Figure 7 As shown, under ideal conditions, the intersection point of the extended teeth after modification still lies on the ideal center plane. This situation is consistent with the attached... Figure 6 The situation is similar in that the symmetry of the left and right helical teeth of the herringbone gear can be controlled in the same way. However, when the left and right helical teeth of the herringbone gear undergo asymmetrical tooth profile modification due to some factors, the normal sectional view of its pitch circle position is shown in the attached figure. Figure 8 As shown, at this time... b i When performing the calculations, the influence of the asymmetric tooth profile modification of the herringbone gear must also be considered. The actual center face position of the herringbone gear after the asymmetric tooth profile modification needs to be accurately calculated. The specific calculation process is as follows (see appendix). Figure 8 As shown: Point C – The intersection of the modified tooth surface and the front face of the left-hand helical tooth; Point D – the intersection of the modified tooth surface and the rear end face of the left-hand helical tooth; Point E – the intersection of the right-hand helical tooth profiled surface and the rear end face; Point F – the intersection of the modified tooth surface and the front face of the right helical tooth; Point G – the point where the extended surfaces of the modified left-hand tooth and the modified right-hand tooth intersect. h — the amount of trimming at the front end of the left-hand and right-hand helical teeth; j — the tooth width of the left-hand and right-hand helical teeth; k——the distance from the rear end face of the left helical tooth / the front end face of the right helical tooth to the ideal center face (i.e., 1 / 2 of the width of the herringbone gear relief groove). x G —The x-coordinate of point G; β —The helix angles of the left-hand and right-hand helical teeth; The coordinate system o(x, y) is as follows: the x-axis is aligned with the gear axis and is positive backward, passing through point E; the y-axis coincides with the ideal center plane of the gear.

[0048] As attached Figure 8 As shown in the figure, both the left-hand and right-hand helical teeth adopt a straight-line tooth profile modification. The modification amount at the front end is h, and the modification amount at the rear end is zero. The tooth surfaces of the left-hand and right-hand helical teeth are asymmetrical after modification, and their extended intersection point G deviates from the ideal center plane. Based on the geometric relationship in the figure, the coordinates of point C are determined to be (-jk, h), the coordinates of point D are (-k, j×tanβ), the coordinates of point E are (j+k, 0), and the coordinates of point F are (k, j×tanβ+h). The equation of line CD (i.e., the modified tooth surface of the left-hand helical tooth) can be determined based on the coordinates of points C and D; the equation of line EF (i.e., the modified tooth surface of the right-hand helical tooth) can be determined based on the coordinates of points E and F; and the x-coordinate of their intersection point G can be obtained by jointly solving the equations of lines CD and EF. x G This allows us to determine the offset of the center plane of the modified gear relative to the ideal center plane and calculate... b i The era entered x G Value calculation is performed to improve calculation accuracy.

[0049] When the tooth directions of the left and right helical teeth are modified using other asymmetric tooth direction forms such as drum shape, a similar method can be adopted. By determining the coordinate positions of key points, the equations of the tooth surfaces of the left and right helical teeth after modification can be determined, and then the coordinate values ​​of the intersection points can be obtained by solving the problem.

[0050] In summary, for herringbone gears undergoing asymmetric tooth profile modification, the offset value of the modification center plane must be considered. x G Dimensions on parallel gear 46 a i and the dimensions on the splitter gear 45 c i The influence of this is used to accurately calculate the position of the center plane of the herringbone teeth, thereby ensuring the axial distance between the two branches. b i Consistency.

[0051] The above description is merely a preferred embodiment of the present invention and is not intended to limit the invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A power split gear load sharing adjustment transmission, characterized by, The power split gear load adjustment transmission device comprises: an output gear (2) and an input gear (3) arranged in sequence and at intervals, and a plurality of power split transmission chains (4) arranged between the output gear (2) and the input gear (3) in a circumferential direction, for splitting the power of the input gear (3) and transmitting the power to the output gear (2); each power split transmission chain (4) comprises a transmission shaft group for circumferential and axial error compensation through flexible deformation, a split gear (45) for splitting power, a parallel gear (46) for parallel power, and an adjusting pad (47) for adjusting the axial distance between the split gear (45) and the parallel gear (46); the transmission shaft group is arranged in extension along the power transmission direction, the parallel gear (46) and the split gear (45) are detachably fixed and arranged on the outer circle of the transmission shaft group in sequence in the axial direction, and the parallel gear (46) is further externally meshed with the output gear (2) for transmission, and the split gear (45) is externally meshed with the input gear (3) for transmission; the adjusting pad (47) is arranged on the outer circle of the transmission shaft group and clamped in the axial direction between the rear end of the split gear (45) and the rear end of the transmission shaft group.

2. The power split gear load adjustment transmission device according to claim 1, wherein the transmission shaft group comprises an elastic shaft (41) arranged in extension along the power transmission direction, and an adapter disc (42) fixedly arranged on the outer circle of the rear end of the elastic shaft (41); the parallel gear (46) is detachably fixed and arranged on the outer circle of the front end of the elastic shaft (41); the split gear (45) is detachably fixed and arranged on the outer circle of the adapter disc (42), and the adjusting pad (47) is arranged on the outer circle of the adapter disc (42) and clamped in the axial direction between the rear end of the split gear (45) and the first shaft shoulder (422) protruding on the rear end of the adapter disc (42).

3. The power split gear load adjustment transmission device according to claim 2, wherein the elastic shaft (41) comprises a hollow thin-walled elastic shaft body, a first flexible thin web plate (411) connected to the rear end of the elastic shaft body, and a first flange connected to the outer ring of the first flexible thin web plate (411); the adapter disc (42) comprises an adapter disc body sleeved on the outer circle of the rear end of the elastic shaft body, a second flexible thin web plate (421) connected to the rear end of the adapter disc body, and a second flange connected to the outer ring of the second flexible thin web plate (421), and the second flange and the first flange are locked and fixed by a plurality of groups of bolts (43) and self-locking nuts (44) arranged in sequence and at intervals in the circumferential direction.

4. The power split gear load adjustment transmission device according to claim 3, wherein the outer circle of the front end of the adapter disc (42) is provided with a first external thread; the inner shaft hole of the split gear (45) has a first shoulder (451) protruding outward, the split gear (45) is connected with the adapter disc (42) through a first spline structure (48), and the outer circle of the front end of the adapter disc (42) is further provided with a first pressing nut (49) to press the first shoulder (451), so that the adjusting pad (47) is pressed between the rear end of the split gear (45) and the first shaft shoulder (422).

5. The power split gear load sharing adjustment transmission according to claim 3, wherein, the outer circle of the front end and the rear end of the elastic shaft (41) is provided with a second external thread and an outwardly convex second shaft shoulder (412) in sequence; the inner shaft hole of the merging gear (46) has an outwardly convex second stop shoulder (461), the merging gear (46) and the elastic shaft (41) are connected through the second spline structure (51), and the outer circle of the front end of the elastic shaft (41) is further provided with a second pressing nut (52) to press the front end of the merging gear (46), so that the second stop shoulder (461) of the merging gear (46) abuts against the second shaft shoulder (412) of the elastic shaft (41) for axial limiting.

6. The power split gear load sharing adjustment transmission according to claim 3, wherein, the output gear (2), the merging gear (46), the split gear (45) and the input gear (3) are all herringbone gears; the two ends of the input gear (3), the two ends of the split gear (45), the two ends of the merging gear (46) and the rear end of the output gear (2) are respectively provided with cylindrical roller bearings (53), and the front end of the merging gear (46) is provided with a ball bearing (54).

7. A power split gear transmission equal load adjustment measure, characterized by The power split gear load sharing adjustment transmission according to claim 6, wherein: I denotes: subscript, i = 1 or 2... or n, wherein 1 denotes the first power split transmission chain (4), 2 denotes the second power split transmission chain (4), n denotes the nth power split transmission chain (4); A i L represents: the axial distance from the center surface of the gear wheel (46) to the rear end surface of the second stop shoulder (461) of the gear wheel (46); b i denotes: axial distance of the center plane of the split gear (45) to the center plane of the coupling gear (46); c i denotes: axial distance of the center face of the split gear (45) to the rear bearing mounting shoulder; d i denotes: width of inner ring of rear bearing of split gear (45) e i Indicates: adjust the thickness of the pad (47); f i denotes: the axial distance from the front end face of the first axial shoulder (422) of the adapter disc (42) to the rear end face of its second flange; g i denotes the axial distance of the first flange front end face of the resilient shaft (41) to the front end face of its second shaft shoulder (412); Axial distance between the center face of the split gear (45) and the center face of the merging gear (46) b i is calculated as follows: ； the power split gear load sharing adjustment measures include replacing the adjustment pad (47) or grinding the thickness of the adjustment pad (47).

8. The power split gear load sharing adjustment measures according to claim 7, wherein, the power split gear load sharing adjustment measures further include setting the structure and thickness of the first flexible thin web (411) and the second flexible thin web (421) so that they can produce axial deformation for compensation after being loaded.

9. The power split gear load sharing adjustment measures according to claim 7, wherein, the power split gear load sharing adjustment measures further include controlling the manufacturing error of the herringbone gear to control the symmetry of the left-handed teeth and the right-handed teeth of the herringbone gear.

10. The power split gear load sharing adjustment measures according to claim 7, wherein, The power split gear transmission device load sharing adjustment measures also include: b i The influence of the tooth direction modification of the herringbone gear is also considered in the calculation, and the position of the actual center surface of the herringbone gear is accurately calculated.

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