An axial rubbing simulation device for the spur gear of a crawler vehicle transmission

Abstract

The present invention discloses an axial rubbing simulation device for the straight gear shaft system of a crawler vehicle transmission, which relates to the field of rotating machinery fault simulation test devices; it includes a distribution shaft A with a dynamic unbalance adjustment disc connected to the outside, and the dynamic unbalance adjustment disc is connected to the input shaft through a gear set; the dynamic unbalance adjustment disc is supported by a bearing A, the large inner diameter hole of the supporting flange is matched with a bearing B, and the small inner diameter hole of the supporting flange is connected to one end of the eddy current shaft A away from the bearing seat through a spline fit; a distribution sleeve-distribution shaft rubbing screw is inserted through the outer side wall of one end of the distribution sleeve A, a distribution sleeve-distribution shaft rubbing half ring is installed at the lower half of one end of the distribution shaft, and a distribution shaft-eddy current shaft rubbing half ring is installed at the upper half of one end of the distribution shaft; a fixed shaft-eddy current shaft rubbing screw is inserted through the side wall of the fixed shaft A, and a fixed shaft-eddy current shaft rubbing ring is connected to one end of the eddy current shaft A close to the fixed shaft A. The present invention can analyze the axial rubbing characteristics of the straight gear shaft system in the crawler vehicle transmission.

Description

Technical Field

[0001] The present invention relates to the field of rotating machinery fault simulation test devices, and particularly to a simulation device for shaft rubbing of spur gears in a crawler vehicle transmission. Background Art

[0002] The transmission system of a crawler vehicle transmission is complex. Among them, rubbing frequently occurs at the seals between the rotors-rotors and rotors-stators of the spur gear shaft system, and there are many influencing factors. Due to the large load and frequent speed changes of the crawler vehicle transmission, the rubbing causes severe vibration of the entire transmission, inducing serious transmission faults. In order to explore the generation mechanism of rubbing and the vibration response characteristics, by testing and simulating different rubbing test signals to carry out fault diagnosis research, it is necessary to build a rubbing simulation device with adjustable quantitative rubbing clearance that retains the original structure of the spur gear system of the crawler vehicle transmission.

[0003] Currently, rubbing test benches mainly carry out rubbing test research on aero-engines and steam turbines. For example, a rubbing device disclosed in a Chinese patent (Publication No.: CN209525097U), a rubbing test method for a dual-rotor test bench disclosed in a Chinese patent (Publication No.: CN106289778A), a rotor-stator rubbing and sand swallowing fault simulation test bench based on electrostatic monitoring disclosed in a Chinese patent (Publication No.: CN114509273A), a small aero-engine multi-point rubbing fault simulation experimental device disclosed in a Chinese patent (Publication No.: CN108709748A), a rubbing force tester for blades-casings in a complex contact state disclosed in a Chinese patent (Publication No.: CN109100068A), an aero-engine low-pressure turbine rotor-stator blade rubbing test bench disclosed in a Chinese patent (Publication No.: CN110926745A), an aero-engine experimental device rubbing device and rubbing test method disclosed in a Chinese patent (Publication No.: CN110285972A), etc. These rubbing test benches are simplified devices for rotor-stator rubbing of aero-engines and steam turbines, and are not suitable for carrying out research on the shaft rubbing characteristics of spur gears in a crawler vehicle transmission, and are even less able to reproduce the specific working conditions of the prototype of the spur gear system in a crawler vehicle transmission. Therefore, it is necessary to build a simulation device for analyzing the shaft rubbing characteristics of spur gears in a crawler vehicle transmission. Summary of the Invention

[0004] The purpose of the present invention is to provide a simulation device for shaft rubbing of spur gears in a crawler vehicle transmission to solve the problems existing in the above-mentioned prior art and be able to analyze the shaft rubbing characteristics of spur gears in a crawler vehicle transmission.

[0005] To achieve the above purpose, the present invention provides the following solution:

[0006] The present invention provides a shaft system rubbing simulation device for spur gears of a crawler vehicle transmission, which is used to analyze the vibration response characteristics and influencing factors of single-point or local rubbing at the seals between the rotors-rotors and rotors-stators of the spur gear system in the crawler vehicle transmission. Single-point rubbing and multi-point coupled rubbing test studies can be carried out. In the prototype - the spur gear system of the crawler vehicle transmission, the outer circumference of the Z34 spur gear shaft is supported by a non-standard bearing, and the non-standard bearing is installed on support A. The Z34 spur gear drives the power input component of the hydraulic torque converter to rotate through spline connection; the power input component of the hydraulic torque converter drives the power output component of the hydraulic torque converter to rotate through hydraulic drive. The power input component of the hydraulic torque converter is supported by bearing A, bearing A is supported by the power output component of the hydraulic torque converter, the power output component of the hydraulic torque converter is supported by bearing B, and bearing B is supported by a fixed shaft; the power input component of the hydraulic torque converter is fixedly connected to the distribution shaft, and the distribution shaft rotates relative to the distribution sleeve, where the distribution sleeve is fixedly connected to support B; the power output component of the hydraulic torque converter drives the eddy current shaft to rotate through spline connection, and the distribution shaft rotates relative to the eddy current shaft. The distribution shaft and the eddy current shaft are rotors, and the distribution sleeve and the fixed shaft are stators. A series of rubbing phenomena occur between the rotors-rotors and rotors-stators of the shaft system where the Z34 spur gear is located. Rubbing occurs at the dynamic seal ring between the fixed shaft and the eddy current shaft, rubbing occurs at the dynamic seal ring between the eddy current shaft and the distribution shaft, and rubbing occurs at the dynamic seal ring between the distribution shaft and the distribution sleeve.

[0007] In order to simulate the above-mentioned single-point collision and multiple simultaneous collisions under the working conditions of the prototype, the present invention proposes a shaft collision simulation device for the spur gear of a tracked vehicle gearbox. On the basis of retaining the main structure of the prototype, in order to facilitate the collision test, some parts of the test box are optimized and modified. The power input component of the torque converter is simplified to a dynamic unbalance adjustment disk, and the power output component of the torque converter is simplified to a supporting flange, that is, the torque converter is removed, and the two move independently. The structure of the present invention includes a distribution shaft A and an eddy current shaft A, and the distribution shaft A and the eddy current shaft A are independently driven by motors respectively. The eddy current shaft A is movably arranged in the distribution shaft A, and the eddy current shaft A can be driven to rotate by the motor. The distribution shaft A is rotatably arranged in the distribution sleeve A. The distribution sleeve A is a hollow shaft with different outer diameter shaft sections according to functional requirements. The distribution shaft A and the distribution sleeve A rotate relative to each other, and the distribution sleeve A is fixedly connected to the housing, and one end of the eddy current shaft A is arranged on the bearing seat; a dynamic unbalance adjustment disk is fixedly connected to the outer side of the distribution shaft A, and the dynamic unbalance adjustment disk is transmission-connected to the input shaft movably arranged on the housing through a gear set, and the output One end of the input shaft is used for connecting with the motor transmission; the dynamic unbalance adjustment disk is supported by bearing A, and bearing A is supported by a supporting flange. The small outer diameter shaft section of the supporting flange cooperates with bearing A, and the large inner diameter hole of the supporting flange cooperates with bearing B, so that the supporting flange is supported by bearing B, and the small inner diameter hole of the supporting flange is connected with the end of the eddy current shaft A away from the bearing seat through a spline; bearing B is supported by a fixed shaft A, and the fixed shaft A is fixedly connected to the box body; a distribution sleeve-distribution shaft rubbing screw is pierced on the outer wall of one end of the distribution sleeve A, a distribution sleeve-distribution shaft rubbing half ring is installed on the lower half of one end of the distribution shaft, and a distribution shaft-eddy current shaft rubbing half ring is installed on the upper half of one end of the distribution shaft; a fixed shaft-eddy current shaft rubbing screw is pierced on the side wall of the fixed shaft A, and the end of the eddy current shaft A close to the fixed shaft A is connected with a fixed shaft-eddy current shaft rubbing ring.

[0008] Optionally, the bearing seat includes a sleeve A, a sealing ring B, a bearing support, a bearing C, a bearing end cover C, a sealing ring C, a sleeve B, and a round nut; one end of the eddy current shaft A is inserted into the bearing C, and sleeve A and sleeve B are provided at both ends of the bearing C, the end of the sleeve A away from the bearing C abuts against the shoulder of the eddy current shaft A, and the end of the sleeve B away from the bearing C is fixedly connected to the round nut; the sleeve A is externally connected to the bearing support, and a sealing ring B is provided at the connecting position between the sleeve A and the bearing, the sleeve B is externally connected to the bearing end cover C, and a sealing ring C is provided at the connecting position between the sleeve B and the bearing end cover C.

[0009] Optionally, the gear set includes a Z45 spur gear and a Z34 spur gear; the input shaft is supported by bearing C and bearing D. Due to the limitation of the box wall thickness, bearing C and bearing D are respectively installed in the inner cavities of flange A and flange B, and flange A and flange B are installed in the box cavity. Bearing C and bearing D are respectively axially positioned by bearing end cover A and bearing end cover B, and the left side of bearing C is positioned by a sleeve; the Z45 spur gear is installed on the input shaft, and the left and right ends of the hub of the Z45 spur gear are positioned by the shaft shoulder of the input shaft and the sleeve; the Z34 spur gear adopts a hollow shaft structure, the inner hole of the Z34 spur gear is an internal spline, the internal spline of the Z34 spur gear is connected to the external spline of the dynamic unbalance adjustment disk, the Z34 spur gear is supported by a non-standard bearing, and the right end of the Z34 spur gear is fixed by a shaft end retaining ring with a spline; the added Z45 spur gear transmits power to the Z34 spur gear, the Z34 spur gear drives the dynamic unbalance adjustment disk through spline connection, the dynamic unbalance adjustment disk is fixedly connected to the distribution shaft A, that is, the rotation of the dynamic unbalance adjustment disk and the distribution shaft A is realized, and the eddy current shaft A is directly driven by the power source.

[0010] Optionally, the dynamic unbalance adjustment disk includes an external spline shaft section and a dynamic unbalance adjustment disk. The dynamic unbalance adjustment disk of the dynamic unbalance adjustment disk is provided with threaded holes of various specifications. M5, M8, M12, M16, M20, M24 and M30 threaded holes are evenly distributed on the circumference R160; on the circumferences R140 and R120, M5 threaded holes are arranged, and they are all in the same radial direction as the M5 threaded holes on the circumference R160. By adding screws and nuts to the dynamic unbalance adjustment disk, the application and adjustment of the dynamic unbalance amount are realized, and the comprehensive influence test of the dynamic unbalance amount on all rubs is carried out.

[0011] Optionally, the Z34 spur gear is supported by a non-standard bearing, and the right end of the Z34 spur gear is fixed by a shaft end retaining ring. The external spline end face of the shaft end retaining ring is used for the axial fixation of the Z34 spur gear, and at the same time it cooperates with the internal spline of the Z34 spur gear. The shaft end retaining ring is connected to the dynamic unbalance adjustment disk by screws.

[0012] Optionally, a replacement shaft head is provided at one end of the eddy current shaft A away from the bearing seat, and the replacement shaft head is located between the eddy current shaft A and the fixed shaft-eddy current shaft rubbing ring.

[0013] Optionally, there is a gap between the circumferential end faces of the distribution sleeve-distribution shaft rubbing half ring and the distribution shaft-eddy current shaft rubbing half ring.

[0014] The simulation device provided by the present invention has two types of functions for adjusting the rubbing gap between the distribution sleeve A and the distribution shaft A, namely: ① equivalently simulating point rubbing through the distribution sleeve-distribution shaft rubbing screw; ② equivalently simulating local rubbing through the distribution sleeve-distribution shaft rubbing half ring.

[0015] When equivalently simulating the point rubbing between the distribution sleeve A and the distribution shaft A through the rubbing screw of the distribution sleeve - distribution shaft, the rubbing screw of the distribution sleeve - distribution shaft is an M8 screw made of different materials. To prevent loosening, a back - tight nut A is installed. For the distribution of the rubbing screws of the distribution sleeve - distribution shaft, the conventional 8 screws are evenly distributed around the whole circumference at an interval of 45°. In addition, from the actual rubbing photos and the common sense of gravity, it can be seen that the rubbing mainly occurs in the lower part. Therefore, 2 more rubbing screws of the distribution sleeve - distribution shaft are symmetrically added in the lower part, and the interval angles from the bottom are both 23°. By precisely controlling the screwing - in amount of the rubbing screws of the distribution sleeve - distribution shaft, the rubbing clearance between the distribution sleeve A and the distribution shaft A is adjusted.

[0016] When equivalently simulating the local rubbing between the distribution sleeve A and the distribution shaft A through the rubbing half - ring of the distribution sleeve - distribution shaft, the rubbing half - ring of the distribution sleeve - distribution shaft is installed on the lower half of the distribution shaft A through the fixing screw A, while the rubbing half - ring of the distribution shaft - eddy current shaft is located in the upper half, and the circumferential end - face distance between the two is 4 mm; the large outer - circumference (rubbing contact) radius of the rubbing half - ring of the distribution sleeve - distribution shaft is equal to the aperture of the distribution sleeve A, that is The small outer - circumference (non - contact) radius is The inner - hole radius is The diameter of the fixing screw A is 2 mm smaller than the diameter of the through - hole on the rubbing half - ring of the distribution sleeve - distribution shaft with which it cooperates. The purpose is to facilitate the adjustment of the position of the rubbing half - ring of the distribution sleeve - distribution shaft to achieve the adjustment of the rubbing clearance between the distribution sleeve A and the distribution shaft A. By precisely controlling the clearance between the large outer - circumference (rubbing contact) of the rubbing half - ring of the distribution sleeve - distribution shaft and the hole wall of the distribution sleeve A, the rubbing clearance between the distribution sleeve A and the distribution shaft A is adjusted.

[0017] The simulation device equivalently simulates the local rubbing between the distribution shaft A and the eddy - current shaft A through the rubbing half - ring of the distribution shaft - eddy current shaft. The rubbing half - ring of the distribution shaft - eddy current shaft is installed on the distribution shaft A through the fixing screw B; the small inner - hole (rubbing contact) radius of the rubbing half - ring of the distribution shaft - eddy current shaft is equal to the radius of the eddy - current shaft A, that is The large inner - hole (non - contact) radius is The outer - circumference radius is The diameter of the fixing screw B is 2 mm smaller than the diameter of the through - hole on the rubbing half - ring of the distribution shaft - eddy current shaft with which it cooperates. The purpose is to facilitate the adjustment of the position of the rubbing half - ring of the distribution shaft - eddy current shaft to equivalently achieve the adjustment of the rubbing clearance between the distribution shaft A and the eddy - current shaft A. By precisely controlling the clearance between the small inner - hole (rubbing contact) of the rubbing half - ring of the distribution shaft - eddy current shaft and the outer - circumference of the eddy - current shaft A, the rubbing clearance between the distribution shaft A and the eddy - current shaft A is adjusted.

[0018] The simulation device has two types of functions for adjusting the rubbing clearance between the fixed shaft A and the eddy - current shaft A, which are: ① equivalently simulating the point rubbing through the rubbing screw of the fixed shaft - eddy current shaft; ② equivalently simulating the local rubbing through the rubbing ring of the fixed shaft - eddy current shaft.

[0019] When the point rubbing between the fixed shaft A and the eddy current shaft A is equivalently simulated by the fixed shaft-eddy current shaft rubbing screw, the fixed shaft-eddy current shaft rubbing screw is an M8 screw. To prevent loosening, a back-tightening screw B is installed. To prevent damage to the body of the eddy current shaft A during the rubbing test, a replacement shaft head is installed at the rubbing part. For the distribution of the fixed shaft-eddy current shaft rubbing screws, the conventional 8 screws are evenly distributed in a full circle at intervals of 45°. 2 fixed shaft-eddy current shaft rubbing screws are symmetrically added at the lower part, and the interval angles from the bottom are both 23°. By precisely controlling the screwing-in amount of the fixed shaft-eddy current shaft rubbing screw, the rubbing clearance between the fixed shaft A and the eddy current shaft A is adjusted.

[0020] When the local rubbing between the fixed shaft A and the eddy current shaft A is equivalently simulated by the fixed shaft-eddy current shaft rubbing ring, the fixed shaft-eddy current shaft rubbing ring adopts an integral ring structure and is installed at the left end of the eddy current shaft A through the fixing screw C. The diameter of the large outer circumference (rubbing contact) is 1 mm smaller than the inner hole diameter of the fixed shaft A, that is The diameter of the small outer circumference (non-contact) is The diameter of the fixing screw C is 2 mm smaller than the diameter of the through hole on the fixed shaft-eddy current shaft rubbing ring it cooperates with. The purpose is to facilitate the adjustment of the position of the fixed shaft-eddy current shaft rubbing ring to equivalently adjust the rubbing clearance between the fixed shaft A and the eddy current shaft A. By precisely controlling the clearance between the large outer circumference (rubbing contact) of the fixed shaft-eddy current shaft rubbing ring and the hole wall of the fixed shaft A, the rubbing clearance between the fixed shaft A and the eddy current shaft A is adjusted.

[0021] The present invention has achieved the following technical effects compared with the prior art:

[0022] The shaft rubbing simulation device for the spur gear of the crawler vehicle transmission provided by the present invention has a simple and reliable structure and is easy to operate; under the condition of retaining the working conditions of the prototype - the spur gear system of the crawler vehicle transmission, it can simulate single rubbing and multiple rubbings; it can simulate two rubbing forms - rubbing and local rubbing, and can also simulate the influence of dynamic unbalance on rubbing; the rubbing clearance can be precisely adjusted. Description of the Drawings

[0023] In order to more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the following will briefly introduce the drawings required to be used in the embodiments. Obviously, the drawings in the following description are only some embodiments of the present invention. For those of ordinary skill in the art, without creative efforts, other drawings can also be obtained based on these drawings.

[0024] Figure 1 It is the Z34 gear shaft system of a certain crawler vehicle transmission spur gear system;

[0025] Figure 2 It is the left axonometric view of a shaft rubbing simulation device for the spur gear of a crawler vehicle transmission;

[0026] Figure 3 It is the right axonometric view of a shaft rubbing simulation device for the spur gear of a crawler vehicle transmission;

[0027] Figure 4 It is the schematic diagram of the internal structure of a shaft rubbing simulation device for the spur gear of a crawler vehicle transmission;

[0028] Figure 5 It is the three-dimensional structure diagram of the dynamic unbalance adjustment disc;

[0029] Figure 6 It is the schematic diagram of the layout of the dynamic unbalance adjustment screw holes on the dynamic unbalance adjustment disc;

[0030] Figure 7 It is the three-dimensional structure diagram of the shaft end retaining ring;

[0031] Figure 8 It is the three-dimensional structure diagram of the support flange;

[0032] Figure 9 It is the three-dimensional structure diagram of the fixed shaft A;

[0033] Figure 10 It is the three-dimensional structure diagram of the flow distribution shaft A;

[0034] Figure 11 It is the three-dimensional structure diagram of the flow distribution sleeve A;

[0035] Figure 12 It is the three-dimensional structure diagram of the eddy current shaft A;

[0036] Figure 13 It is the schematic diagram of the rubbing clearance adjustment mechanism between the flow distribution sleeve A and the flow distribution shaft A and the rubbing clearance adjustment mechanism between the flow distribution shaft A and the eddy current shaft A Figure 1 ;

[0037] Figure 14 It is the schematic diagram of the layout of the rubbing screws between the flow distribution sleeve and the flow distribution shaft;

[0038] Figure 15 It is the schematic diagram of the rubbing clearance adjustment mechanism between the flow distribution sleeve A and the flow distribution shaft A and the rubbing clearance adjustment mechanism between the flow distribution shaft A and the eddy current shaft A Figure 2 ;

[0039] Figure 16 It is Figure 15 the A-A sectional view of;

[0040] Figure 17 It is the three-dimensional structure diagram of the rubbing ring between the flow distribution sleeve and the flow distribution shaft;

[0041] Figure 18 It is the three-dimensional structure diagram of the rubbing ring between the flow distribution shaft and the eddy current shaft;

[0042] Figure 19 It is a schematic diagram of the rubbing clearance adjustment mechanism between the fixed shaft A and the eddy current shaft A Figure 1 ;

[0043] Figure 20 It is a schematic diagram of the arrangement of the rubbing screws between the fixed shaft and the eddy current shaft;

[0044] Figure 21 It is a schematic diagram of the rubbing clearance adjustment mechanism between the fixed shaft A and the eddy current shaft A Figure 2 ;

[0045] Figure 22 It is Figure 21 The B-B sectional view of;

[0046] Figure 23 It is a three-dimensional structure diagram of the rubbing ring between the fixed shaft and the eddy current shaft;

[0047] Figure 24 It is a schematic diagram of the rubbing clearance adjustment process when the rubbing screws between the flow distribution sleeve and the flow distribution shaft equivalently simulate the point rubbing between the flow distribution sleeve A and the flow distribution shaft A;

[0048] Figure 25 It is a schematic diagram of the rubbing clearance adjustment when the rubbing half-ring between the flow distribution sleeve and the flow distribution shaft equivalently simulates the local rubbing between the flow distribution sleeve A and the flow distribution shaft A;

[0049] Figure 26 It is Figure 25 The A-A sectional view of;

[0050] Figure 27 It is a schematic diagram of the rubbing clearance adjustment when the rubbing half-ring between the flow distribution shaft and the eddy current shaft equivalently simulates the local rubbing between the flow distribution shaft A and the eddy current shaft A;

[0051] Figure 28 It is Figure 27 The A-A sectional view of;

[0052] Figure 29 It is a schematic diagram of the rubbing clearance adjustment process when the rubbing screws between the fixed shaft and the eddy current shaft equivalently simulate the point rubbing between the fixed shaft A and the eddy current shaft A;

[0053] Figure 30 It is a schematic diagram of the rubbing clearance adjustment when the rubbing ring between the fixed shaft and the eddy current shaft equivalently simulates the local rubbing between the fixed shaft A and the eddy current shaft A;

[0054] Figure 31 It is Figure 30 The sectional view of;

[0055] Description of reference numerals: 1 - support, 2 - non-standard bearing, 3 - Z34 spur gear, 4 - shaft end retaining ring, 5 - flow distribution sleeve, 6 - flow distribution shaft, 7 - eddy current shaft, 8 - support B, 9 - power input component of torque converter, 10 - bearing A, 11 - power output component of torque converter, 12 - bearing B, 13 - fixed shaft, 14 - housing, 15 - Z45 spur gear, 16 - flange A, 17 - bearing end cover B, 18 - sleeve, 19 - bearing C, 20 - input shaft, 21 - flow distribution shaft A, 22 - flow distribution sleeve A, 23 - rubbing semi-ring between flow distribution sleeve and flow distribution shaft, 24 - fixing screw A, 25 - fixing screw B, 26 - rubbing semi-ring between flow distribution shaft and eddy current shaft, 27 - back-tightening nut A, 28 - rubbing screw between flow distribution sleeve and flow distribution shaft, 29 - dynamic unbalance adjustment disc, 30 - support flange, 31 - fixed shaft A, 32 - rubbing screw between fixed shaft and eddy current shaft, 33 - back-tightening nut B, 34 - shaft head, 35 - rubbing ring between fixed shaft and eddy current shaft, 36 - fixing screw C, 37 - flange B, 38 - bearing end cover A, 39 - bearing D, 40 - end cover sealing device, 41 - sleeve A, 42 - sealing ring B, 43 - bearing support, 44 - bearing C, 45 - bearing end cover C, 46 - sealing ring C, 47 - sleeve B, 48 - round nut, 49 - eddy current shaft A, 50 - feeler gauge A, 51 - tooling A, 52 - copper sheet A, 53 - copper sheet B, 54 - feeler gauge B, 55 - tooling B, 56 - copper sheet C. Detailed implementation mode

[0056] The following will clearly and completely describe the technical solutions in the embodiments of the present invention with reference to the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all the embodiments. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present invention without creative efforts shall fall within the protection scope of the present invention.

[0057] The purpose of the present invention is to provide a shafting rubbing simulation device for spur gears in a crawler vehicle transmission to solve the problems existing in the above-mentioned prior art and be able to analyze the shafting rubbing characteristics of spur gears in a crawler vehicle transmission.

[0058] To make the above-mentioned objects, features, and advantages of the present invention more obvious and understandable, the present invention will be further described in detail below with reference to the accompanying drawings and specific implementation modes.

[0059] As Figure 1As shown, in the prototype - the spur gear system of the crawler vehicle transmission, a series of rubbing phenomena occur between the rotor - rotor and rotor - stator of the shafting where the Z34 spur gear is located. The outer circumference of the 3 - shaft section of the Z34 spur gear 3 is supported by a non - standard bearing 2, and the non - standard bearing 2 is supported and installed on the support A1. The Z34 spur gear 3 is connected to the power input component 9 of the hydraulic torque converter through an internal spline. The right end of the Z34 spur gear 3 is fixed by an axle end retaining ring 4; the power input component 9 of the hydraulic torque converter is supported by a bearing A10, the bearing A10 is supported by the power output component 11 of the hydraulic torque converter, the power output component 11 of the hydraulic torque converter is supported by a bearing B12, and the bearing B12 is supported by a fixed shaft 13; the power input component 9 of the hydraulic torque converter is fixedly connected to the distribution shaft 6, and the distribution shaft 6 rotates relative to the distribution sleeve 5, where the distribution sleeve 5 is fixedly connected to the support B8; at the same time, the distribution shaft 6 also rotates relative to the eddy current shaft 7, where the eddy current shaft 7 is connected to the power output component 11 of the hydraulic torque converter through a spline. The movement route is as follows: the Z34 spur gear 3 drives the power input component 9 of the hydraulic torque converter through an internal spline, and the distribution shaft 6 rotates synchronously with the power input component 9 of the hydraulic torque converter; the power input component 9 of the hydraulic torque converter hydraulically drives the power output component 11 of the hydraulic torque converter, and the power output component 11 of the hydraulic torque converter drives the eddy current shaft 7 through a spline. In this support shafting rubbing system, the distribution shaft 6 and the eddy current shaft 7 are rotors, the distribution sleeve 5 and the fixed shaft 13 are stators, and rubbing occurs at the dynamic seal ring between the fixed shaft 13 and the eddy current shaft 7, between the eddy current shaft 7 and the distribution shaft 6, and between the distribution shaft 6 and the distribution sleeve 5.

[0060] In order to simulate the above - mentioned single - point rubbing and multi - point simultaneous rubbing under the condition of retaining the prototype working conditions, the present invention proposes a shafting rubbing simulation device for the spur gear of the crawler vehicle transmission. The overall structure is as Figure 2 and Figure 3 shown, and the specific internal structure is as Figure 4 shown. The specific scheme is as follows.

[0061] As Figure 4 shown, the structures of the power input component of the hydraulic torque converter ( Figure 1 shown as 9) and the power output component of the hydraulic torque converter ( Figure 1 shown as 11) are simplified, and are respectively replaced by a passive unbalance adjustment disk 29 and a support flange disk 30. The two move independently, and the distribution shaft A21 and the eddy current shaft A49 are respectively independently driven by motors. The power input path of the distribution shaft A21 is as follows: the motor transmits power to the Z34 spur gear 3 through the input shaft 20 and the Z45 spur gear 15 thereon. The Z34 spur gear 3 is connected to the dynamic unbalance adjustment disk 29 through an internal spline, and the dynamic unbalance adjustment disk 29 is fixedly connected to the distribution shaft A21, that is, the rotation of the dynamic unbalance adjustment disk 29 and the distribution shaft A21 is realized. The power input path of the eddy current shaft A49 is as follows: the motor directly drives the eddy current shaft A49.

[0062] As shown Figure 4 in FIG. 1, the input shaft 20 is supported by a bearing C19 and a bearing D39, which are respectively installed in the inner cavities of a flange A16 and a flange B37. The flange A16 and the flange B37 are installed in the hole cavity of a housing 14. The bearing C19 and the bearing D39 are respectively axially positioned by a bearing end cover A38 and a bearing end cover B17. A gland seal device 40 is arranged inside the bearing end cover A38. The left side of the bearing C19 is positioned by a sleeve 18. A Z45 spur gear 15 is installed on the input shaft 20, and the left and right ends of its hub are positioned by the shaft shoulder of the input shaft 20 and the sleeve 18.

[0063] As shown Figure 4 in FIG. 2, the Z34 spur gear 3 adopts a hollow shaft structure, the inner hole is an internal spline, and is connected to a dynamic unbalance adjustment disk 29 through a spline connection. The three-dimensional structure of the dynamic unbalance adjustment disk 29 is as shown Figure 5 in FIG. 3. It mainly consists of an external spline shaft section and a dynamic unbalance adjustment disk. By adding screws and nuts to the dynamic unbalance adjustment disk of the dynamic unbalance adjustment disk 29, the application and adjustment of the dynamic unbalance amount are realized, and the comprehensive influence of the dynamic unbalance amount of the torque converter on all rubs is carried out. In order to realize the adjustment of various dynamic unbalance amounts, the dynamic unbalance adjustment disk of the dynamic unbalance adjustment disk 29 is provided with threaded holes of various specifications, as shown Figure 6 in FIG. 4. 2-M5, 2-M8, 2-M12, 2-M16, 2-M20, 2-M24 and 2-M30 threaded holes are evenly distributed and symmetrically arranged on the circumference R160. The marks in the figure are 2-M5 symmetry, 2-M8 symmetry, 2-M12 symmetry, 2-M16 symmetry, 2-M20 symmetry, 2-M24 symmetry and 2-M30 symmetry; on the circumferences R140 and R120, 2-M5 threaded holes are symmetrically arranged. The marks in the figure are 2-M5 symmetry, and they are all in the same radial direction as the 2-M5 threaded holes on the circumference R160.

[0064] As shown Figure 4 in FIG. 5, the Z34 spur gear 3 is supported by a non-standard bearing 2. The right end of the Z34 spur gear 3 is fixed by a shaft end retaining ring 4. The three-dimensional schematic diagram of the shaft end retaining ring 4 is as shown Figure 7 in FIG. 6. The external spline end face of the shaft end retaining ring 4 is used for the axial fixation of the Z34 spur gear 3, and at the same time cooperates with the internal spline of the Z34 spur gear 3 to realize the enhancement of circumferential power transmission. The shaft end retaining ring 4 is connected to the dynamic unbalance adjustment disk 29 by screws.

[0065] As shown Figure 4 in FIG. 7, the dynamic unbalance adjustment disk 29 is supported by a bearing A10, and the bearing A10 is supported by a support flange 30. The three-dimensional structure of the support flange 30 is as shown Figure 8As shown, the small outer diameter shaft section of the support flange 30 is fitted with bearing A10, and the large inner diameter hole of the support flange 30 is fitted with bearing B12, so that the support flange 30 is supported by bearing B12. The small inner diameter hole of the support flange 30 is an internal spline, which is fitted with the external spline of the eddy current shaft A49.

[0066] As Figure 4 shown, bearing B12 is supported by the fixed shaft A31, and the fixed shaft A31 is fixedly connected to the box body 14. The three-dimensional structure of the fixed shaft A31 is as Figure 9 shown, and it is made into a hollow shaft with different outer diameter shaft sections according to functional requirements.

[0067] As Figure 4 shown, the flow distribution shaft A21 is fixedly connected to the dynamic unbalance adjustment disc 29, and the two rotate synchronously. The three-dimensional structure of the flow distribution shaft A21 is as Figure 10 shown. Due to lubrication requirements, the flow distribution shaft A21 is provided with multiple forms of holes and grooves.

[0068] As Figure 4 shown, the flow distribution sleeve A22 is fixedly connected to the box body 14, and the flow distribution shaft A21 rotates relative to the flow distribution sleeve A22. The three-dimensional structure of the flow distribution sleeve A22 is as Figure 11 shown, and it is made into a hollow shaft with different outer diameter shaft sections according to functional requirements.

[0069] As Figure 4 shown, the right end of the eddy current shaft A49 is supported by a bearing seat made of sleeve A41, seal ring B42, bearing bracket 43, bearing C44, bearing end cover C45, seal ring C46, sleeve B47, and round nut 48. The left end of the eddy current shaft A49 is connected to the support flange 30 through a spline to achieve floating support. The three-dimensional structure of the eddy current shaft A49 is as Figure 12 shown. The eddy current shaft A49 is made into a hollow shaft with different outer diameter shaft sections according to functional requirements, and is provided with an external spline shaft section and an external thread shaft section.

[0070] As Figure 13 shown, the simulation device has two types of functions for adjusting the rubbing clearance between the flow distribution sleeve A22 and the flow distribution shaft A21, namely: ① equivalently simulating the point rubbing between the flow distribution sleeve A22 and the flow distribution shaft A21 through the flow distribution sleeve-flow distribution shaft rubbing screw 28; ② equivalently simulating the local rubbing between the flow distribution sleeve A22 and the flow distribution shaft A21 through the flow distribution sleeve-flow distribution shaft rubbing half ring 23.

[0071] As Figure 13 shown, when equivalently simulating the point rubbing between the flow distribution sleeve A22 and the flow distribution shaft A21 through the flow distribution sleeve-flow distribution shaft rubbing screw 28, the flow distribution sleeve-flow distribution shaft rubbing screw 28 is made into an M8 screw with different materials (copper, polytetrafluoroethylene, cast iron). In order to prevent loosening, each flow distribution sleeve-flow distribution shaft rubbing screw 28 is installed with a back-tightening nut A27. As Figure 14As shown, the rubbing screws 28 between the flow distribution sleeve and the flow distribution shaft are arranged circumferentially. The conventional arrangement interval is 45°. In addition, from the actual rubbing photos and the common sense of gravity, it can be known that the rubbing mainly occurs in the lower part. Therefore, two rubbing screws are symmetrically added in the lower part, and the interval angles from the bottom are both 23°.

[0072] As Figure 13 and Figure 15 、 Figure 16 shown, when the rubbing half-ring 23 between the flow distribution sleeve and the flow distribution shaft is used to equivalently simulate the local rubbing between the flow distribution sleeve A22 and the flow distribution shaft A21, the rubbing half-ring 23 between the flow distribution sleeve and the flow distribution shaft is installed on the lower half of the flow distribution shaft A21, while the rubbing half-ring 26 between the flow distribution shaft and the eddy current shaft is located on the upper half. The circumferential end face spacing between the two is 4 mm; the large outer circumference (rubbing contact) radius of the rubbing half-ring 23 between the flow distribution sleeve and the flow distribution shaft is The small outer circumference (non-contact) radius is The inner hole radius is The diameter of the threaded through-hole is φ7, and the fixing screw A24 of the rubbing half-ring 23 between the flow distribution sleeve and the flow distribution shaft is M5. The purpose of the diameter of the threaded through-hole of the rubbing half-ring 23 between the flow distribution sleeve and the flow distribution shaft being larger than the diameter of the fixing screw A24 is to facilitate the adjustment of the position of the rubbing half-ring 23 between the flow distribution sleeve and the flow distribution shaft, so as to equivalently realize the adjustment of the rubbing gap between the flow distribution sleeve A22 and the flow distribution shaft A21; the total length of the rubbing half-ring 23 between the flow distribution sleeve and the flow distribution shaft is 10, and the length of the large outer circumference (rubbing contact) is 4. The three-dimensional structure of the rubbing half-ring 23 between the flow distribution sleeve and the flow distribution shaft is as Figure 17 shown.

[0073] As Figure 13 and Figure 15 、 Figure 16 shown, the simulation device equivalently simulates the local rubbing between the flow distribution shaft A21 and the eddy current shaft A49 through the rubbing half-ring 26 between the flow distribution shaft and the eddy current shaft. The rubbing half-ring 26 between the flow distribution shaft and the eddy current shaft is installed on the upper half of the flow distribution shaft A21, while the rubbing half-ring 23 between the flow distribution sleeve and the flow distribution shaft is installed on the lower half of the flow distribution shaft A21. The circumferential end face spacing between the two is 4 mm; the small inner hole (rubbing contact) radius of the rubbing half-ring 26 between the flow distribution shaft and the eddy current shaft is The large inner hole (non-contact) radius is The outer circumference radius is The diameter of the threaded through-hole is Φ7, and the fixing screw B25 of the rubbing half-ring 26 between the flow distribution shaft and the eddy current shaft is M5. The purpose of the diameter of the threaded through-hole of the rubbing half-ring 26 between the flow distribution shaft and the eddy current shaft being larger than the diameter of the fixing screw B25 is to facilitate the adjustment of the position of the rubbing half-ring 26 between the flow distribution shaft and the eddy current shaft, so as to equivalently realize the adjustment of the rubbing gap between the flow distribution shaft A21 and the eddy current shaft A49; the total length of the rubbing half-ring 26 between the flow distribution shaft and the eddy current shaft is 10, and the length of the small inner hole (rubbing contact) is 4. The three-dimensional structure of the rubbing half-ring 26 between the flow distribution shaft and the eddy current shaft is as Figure 18 shown.

[0074] As shown in Figure 19 the figure, the simulation device has two functions for adjusting the rubbing clearances of the fixed shaft A31 and the eddy current shaft A49, namely: ① equivalently simulating the point rubbing between the fixed shaft A31 and the eddy current shaft A49 through the fixed shaft-eddy current shaft rubbing screw 32; ② equivalently simulating the partial rubbing between the fixed shaft A31 and the eddy current shaft A49 through the fixed shaft-eddy current shaft rubbing ring 35.

[0075] As shown in Figure 19 the figure, when equivalently simulating the point rubbing between the fixed shaft A31 and the eddy current shaft A49 through the fixed shaft-eddy current shaft rubbing screw 32, the fixed shaft-eddy current shaft rubbing screw 32 uses different materials (copper, polytetrafluoroethylene, cast iron) to support the M8 screw. To prevent loosening, a locking nut B33 is installed for each fixed shaft-eddy current shaft rubbing screw 32. At the same time, to prevent damage to the body of the eddy current shaft A49 during the rubbing test, a replaceable shaft head 34 is added to the left end of the eddy current shaft A49. As shown in Figure 20 the figure, the fixed shaft-eddy current shaft rubbing screws 32 are arranged circumferentially. The conventional arrangement interval is 45°. In addition, it can be seen from the actual rubbing photos and the common sense of gravity that the rubbing mainly occurs at the lower part. Therefore, two rubbing screws are symmetrically added at the lower part, and the interval angles from the bottom are both 23°.

[0076] As shown in Figure 19 and Figure 21 、 Figure 22 the figure, when equivalently simulating the partial rubbing between the fixed shaft A31 and the eddy current shaft A49 through the fixed shaft-eddy current shaft rubbing ring 35, the fixed shaft-eddy current shaft rubbing ring 35 adopts an integral ring structure. The large outer circumference (rubbing contact) diameter is The small outer circumference (non-contact) diameter is The threaded through-hole diameter is φ7, and the fixing screw C36 of the fixed shaft-eddy current shaft rubbing ring 35 is M5. The purpose of the threaded through-hole diameter of the fixed shaft-eddy current shaft rubbing ring 35 being larger than the diameter of the fixing screw C36 is to facilitate the adjustment of the position of the fixed shaft-eddy current shaft rubbing ring 35 to equivalently achieve the adjustment of the rubbing clearance between the fixed shaft A31 and the eddy current shaft A49; the total length of the eddy current fixed shaft-eddy current shaft rubbing ring 35 is 10, and the length of the large outer circumference (rubbing contact) is 4. The three-dimensional structure of the fixed shaft-eddy current shaft rubbing ring 35 is as shown in Figure 23 the figure.

[0077] The operation method of the present invention:[[]]

[0078] A shafting rubbing simulation device for a track vehicle gearbox provided by the present invention is used to simulate single rubbing or multiple rubbings of the port plate A22 and the port shaft A21 rubbing, the port shaft A21 and the eddy current shaft A49 rubbing, and the fixed shaft A31 and the eddy current shaft A49 rubbing. The specific methods for adjusting the rubbing clearance and the comprehensive dynamic unbalance are as follows.

[0079] 1. The wear and friction screw 28 of the flow distribution sleeve - flow distribution shaft equivalently simulates the adjustment of the wear and friction gap when the flow distribution sleeve A22 and the flow distribution shaft A21 are in point contact and wear.

[0080] Step 1: Determine the zero-gap reference.

[0081] As Figure 24 shown in (a) of, first, in the standby static state, the tooling A51 fills the gap between the flow distribution sleeve - flow distribution shaft A22 - flow distribution shaft A21 on the opposite side of the wear and friction screw 28 of the flow distribution sleeve - flow distribution shaft; then the wear and friction screw 28 of the flow distribution sleeve - flow distribution shaft is screwed in until it contacts the flow distribution shaft A21; subsequently, the remaining gap between the head of the wear and friction screw 28 of the flow distribution sleeve - flow distribution shaft and the back-tightening nut A27 is filled with a feeler gauge A50. Note: The length of the wear and friction screw 28 of the flow distribution sleeve - flow distribution shaft and the size of the tooling A51 are determined after all components are processed.

[0082] Step 2: Adjust the wear and friction gap.

[0083] As Figure 24 shown in (b) of, by increasing the thickness of the feeler gauge A50 between the head of the wear and friction screw 28 of the flow distribution sleeve - flow distribution shaft and the back-tightening nut A27, the adjustment of the point contact and wear gap between the flow distribution sleeve A22 and the flow distribution shaft A21 is quantitatively achieved.

[0084] 2. The wear and friction half-ring 23 of the flow distribution sleeve - flow distribution shaft equivalently simulates the adjustment of the wear and friction gap when the flow distribution sleeve A22 and the flow distribution shaft A21 are locally in contact and wear.

[0085] Step 1: Determine the zero-gap reference.

[0086] As Figure 25 、 Figure 26 shown, in the standby static state, under the action of gravity, ensure that the large outer circumference of the wear and friction half-ring 23 of the flow distribution sleeve - flow distribution shaft contacts the inner wall hole of the flow distribution sleeve A22, that is, the zero-gap in the initial state of wear and friction is achieved.

[0087] Step 2: Adjust the wear and friction gap.

[0088] As Figure 25 、 Figure 26 shown, in the state where the fixing screw A24 is not tightened, by quantitatively adjusting the gap between the wear and friction half-ring 23 of the flow distribution sleeve - flow distribution shaft and the inner hole wall of the flow distribution sleeve A22 with a copper sheet A52, the adjustment of the wear and friction gap is achieved. The diameter difference between the threaded hole of the wear and friction half-ring 23 of the flow distribution sleeve - flow distribution shaft and the fixing screw A24 is 2 mm.

[0089] 3. The wear and friction half-ring 26 of the flow distribution shaft - eddy current shaft equivalently simulates the adjustment of the wear and friction gap when the flow distribution shaft A21 and the eddy current shaft A49 are locally in contact and wear.

[0090] Step 1: Determine the zero-gap reference.

[0091] In the standby static state, under the action of gravity, it is ensured that the small inner hole of the flow distribution shaft - eddy current shaft rubbing half - ring 26 contacts the outer circumference of the eddy current shaft A49, that is, the zero - clearance in the initial rubbing state is achieved.

[0092] Step 2: Adjustment of the rubbing clearance.

[0093] As Figure 27 、 Figure 28 shown, in the state where the fixing screw B25 is not tightened, the clearance between the flow distribution shaft - eddy current shaft rubbing half - ring 26 and the outer circumference of the eddy current shaft A49 is quantitatively adjusted through the copper sheet B53, so as to achieve the adjustment of the rubbing clearance. The diameter difference between the threaded hole of the flow distribution shaft - eddy current shaft rubbing half - ring 26 and the fixing screw B25 is 2 mm.

[0094] 4. The fixed - shaft - eddy current shaft rubbing screw 32 equivalently simulates the adjustment of the rubbing clearance when the fixed shaft A31 and the eddy current shaft A49 are in point rubbing

[0095] Step 1: Determination of the zero - clearance reference.

[0096] As Figure 29 shown in (a) of [reference], first, in the standby static state, the tooling B55 fills the clearance between the fixed shaft A31 and the eddy current shaft A49 on the opposite side of the fixed - shaft - eddy current shaft rubbing screw 32; then the fixed - shaft - eddy current shaft rubbing screw 32 is screwed in until it contacts the eddy current shaft A49; subsequently, the remaining clearance between the fixed - shaft - eddy current shaft rubbing screw 32 and the back - tight nut B33 is filled with a feeler gauge B54. Note: The length of the fixed - shaft - eddy current shaft rubbing screw 32 and the size of the tooling B55 are determined after all components are processed.

[0097] Step 2: Adjustment of the rubbing clearance.

[0098] As Figure 29 shown in (b) of [reference], by increasing the thickness of the feeler gauge B54 between the fixed - shaft - eddy current shaft rubbing screw 32 and the back - tight nut B33, the rubbing clearance is quantitatively achieved.

[0099] 5. The fixed - shaft - eddy current shaft rubbing ring 35 equivalently simulates the adjustment of the rubbing clearance when the fixed shaft A31 and the eddy current shaft A49 are in local rubbing

[0100] Step 1: Determination of the zero - clearance reference.

[0101] As Figure 30 、 Figure 31 shown, in the standby static state, under the action of gravity, it is ensured that the large outer circumference of the fixed - shaft - eddy current shaft rubbing ring 35 contacts the inner wall hole of the fixed shaft A31, that is, the zero - clearance in the initial rubbing state is achieved.

[0102] Step 2: Adjustment of the rubbing clearance.

[0103] As Figure 30 、 Figure 31As shown in the figure, when the fixing screw C36 is not tightened, the gap between the shaft-vortex shaft rubbing ring 35 and the inner hole wall of the fixed shaft A31 is quantitatively adjusted by the copper sheet C56 to achieve the adjustment of the rubbing gap. The diameter difference between the threaded hole of the fixed shaft-vortex shaft rubbing ring 35 and the fixing screw C36 is 2 mm.

[0104] 6. Adjustment of the combined dynamic unbalance

[0105] As Figure 5 shown in the figure, by screwing the corresponding bolts and nuts into the threaded holes at different positions of the dynamic unbalance adjustment disc 29, different combined dynamic unbalance adjustments can be obtained, so as to affect the rubbing states of the flow distribution sleeve A22 and the flow distribution shaft A21, the flow distribution shaft A21 and the vortex shaft A49, and the fixed shaft A31 and the vortex shaft A49.

[0106] 7. Conducting tests on single rubbing or multiple rubbings

[0107] 1. Conduct a single rubbing test on the flow distribution sleeve A22 and the flow distribution shaft A21. Only start the driving motor of the input shaft 20, that is, only the flow distribution sleeve A22 rotates, while the vortex shaft A49 does not rotate. By adjusting the screwing depth of the flow distribution sleeve-flow distribution shaft rubbing screw 28 or the initial rubbing gap between the flow distribution sleeve-flow distribution shaft rubbing half-ring 23 and the inner hole wall of the flow distribution sleeve A22, the rubbing adjustment between the flow distribution sleeve A22 and the flow distribution shaft A21 is achieved.

[0108] 2. Conduct a single rubbing test on the flow distribution shaft A21 and the vortex shaft A49. Start the driving motor of the input shaft 20 and the driving motor of the vortex shaft A49 at the same time, that is, the flow distribution shaft A21 and the vortex shaft A49 rotate simultaneously. By adjusting the initial rubbing gap between the flow distribution shaft-vortex shaft rubbing half-ring 26 and the outer circumference of the vortex shaft A49, the rubbing adjustment between the flow distribution shaft A21 and the vortex shaft A49 is achieved;

[0109] 3. Conduct a single rubbing test on the fixed shaft A31 and the vortex shaft A49. Only start the driving motor of the vortex shaft A49. By adjusting the screwing depth of the fixed shaft-vortex shaft rubbing screw 32 or the initial rubbing gap between the fixed shaft-vortex shaft rubbing ring 35 and the inner hole wall of the fixed shaft A31, the rubbing adjustment between the fixed shaft A31 and the vortex shaft A49 is achieved;

[0110] 4. Conduct a multiple rubbing test. Start the driving motor of the input shaft 20 and the driving motor of the vortex shaft A49 at the same time, that is, the flow distribution shaft A21 and the vortex shaft A49 rotate simultaneously. By screwing the corresponding bolts and nuts into the threaded holes at different positions of the dynamic unbalance adjustment disc 29, the application and adjustment of the dynamic unbalance are achieved, and the comprehensive influence test of the dynamic unbalance on all rubbings is conducted.

[0111] In the description of the present invention, it should be noted that the orientation or positional relationship indicated by the terms "center", "top", "bottom", "left", "right", "vertical", "horizontal", "inner", "outer", etc. is based on the orientation or positional relationship shown in the drawings. It is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation. Therefore, it should not be construed as a limitation to the present invention. In addition, the terms "first" and "second" are only used for descriptive purposes and cannot be construed as indicating or implying relative importance.

[0112] Specific examples are used in the present invention to elaborate on the principles and implementation manners of the present invention. The description of the above embodiments is only for helping to understand the method and its core idea of the present invention; at the same time, for those of ordinary skill in the art, according to the idea of the present invention, there will be changes in the specific implementation manners and application scopes. In summary, the content of this specification should not be construed as a limitation to the present invention.

Claims

1. A shafting rubbing simulation device for spur gears of a crawler vehicle transmission, characterized in that: It includes a distribution shaft A and an eddy current shaft A, wherein the eddy current shaft A is movably arranged in the distribution shaft A, and the eddy current shaft A can be driven to rotate by a motor, and the distribution shaft A is rotatably arranged in the distribution sleeve A, and the distribution sleeve A is fixedly connected to the housing, and one end of the eddy current shaft A is arranged on the bearing seat; a dynamic unbalance adjustment disk is fixedly connected to the outer side of the distribution shaft A, and the dynamic unbalance adjustment disk is transmission-connected to an input shaft movably arranged on the housing through a gear set, and one end of the input shaft is used for transmission connection with the motor; the dynamic unbalance adjustment disk is supported by a bearing A, and the bearing A is supported by a supporting flange, and the small outer diameter shaft section of the supporting flange cooperates with the bearing A, supporting The large inner diameter hole of the flange cooperates with the bearing B to realize that the supporting flange is supported by the bearing B, and the small inner diameter hole of the supporting flange is connected to the end of the eddy current shaft A away from the bearing seat through a spline; the bearing B is supported by the fixed shaft A, and the fixed shaft A is fixedly connected to the box body; a distribution sleeve-distribution shaft rubbing screw is pierced on the outer wall of one end of the distribution sleeve A, a distribution sleeve-distribution shaft rubbing half ring is installed on the lower half of one end of the distribution shaft, and a distribution shaft-eddy current shaft rubbing half ring is installed on the upper half of one end of the distribution shaft; a fixed shaft-eddy current shaft rubbing screw is pierced on the outer wall of the fixed shaft A, and the end of the eddy current shaft A close to the fixed shaft A is connected with a fixed shaft-eddy current shaft rubbing ring.

2. The shaft rubbing simulation device for the spur gear of the crawler vehicle gearbox according to claim 1, characterized in that: The bearing seat includes a sleeve A, a sealing ring B, a bearing support, a bearing C, a bearing end cover C, a sealing ring C, a sleeve B, and a round nut; one end of the eddy current shaft A is inserted into the bearing C, and sleeves A and sleeves B are provided at both ends of the bearing C, the end of the sleeve A away from the bearing C abuts against the shoulder of the eddy current shaft A, and the end of the sleeve B away from the bearing C is fixedly connected to the round nut; the sleeve A is externally connected to the bearing support, and a sealing ring B is provided at the connecting position between the sleeve A and the bearing, the sleeve B is externally connected to the bearing end cover C, and a sealing ring C is provided at the connecting position between the sleeve B and the bearing end cover C.

3. The shaft rubbing simulation device for the spur gear in the crawler vehicle transmission according to claim 1, characterized in that: The gear set includes a Z45 spur gear and a Z34 spur gear; the input shaft is supported by a bearing C and a bearing D, which are respectively mounted in the inner cavities of a flange A and a flange B, which are respectively mounted in the bore of a housing, and the bearings C and D are respectively axially positioned by a bearing end cover A and a bearing end cover B, and the left side of the bearing C is positioned by a sleeve; the Z45 spur gear is mounted on the input shaft, and the left and right ends of the Z45 spur gear hub are positioned by the input shaft shoulder and the sleeve; the Z34 spur gear adopts a hollow shaft structure, the inner hole of the Z34 spur gear is an internal spline, and the internal spline of the Z34 spur gear is connected to the external spline of the dynamic unbalance adjustment disk.

4. The shaft rubbing simulation device for the spur gear of the crawler vehicle transmission according to claim 3, characterized in that: The dynamic unbalance adjustment disk comprises an external spline shaft section and a dynamic unbalance adjustment disk. The dynamic unbalance adjustment disk of the dynamic unbalance adjustment disk is arranged with threaded holes of various specifications. By adding screws and nuts to the dynamic unbalance adjustment disk of the dynamic unbalance adjustment disk, the dynamic unbalance can be applied and adjusted.

5. The shafting rubbing simulation device for the spur gear of the crawler vehicle transmission according to claim 4, wherein: The Z34 spur gear is supported by a non-standard bearing. The right end of the Z34 spur gear is fixed by a shaft end retaining ring. The end face of the external spline of the shaft end retaining ring is used for the axial fixation of the Z34 spur gear and is also matched with the internal spline of the Z34 spur gear. The shaft end retaining ring is connected to the dynamic unbalance adjustment disc by screws.

6. The shaft rubbing simulation device for the spur gear of the crawler vehicle transmission according to claim 1, characterized in that: A replacement shaft head is provided at one end of the eddy current shaft A away from the bearing housing, and the replacement shaft head is located between the eddy current shaft A and the fixed shaft-eddy current shaft rubbing ring.

7. The shaft rubbing simulation device for the spur gear of the crawler vehicle transmission according to claim 1, characterized in that: There is a gap between the circumferential end faces of the flow distribution sleeve-flow distribution shaft rubbing half ring and the flow distribution shaft-eddy current shaft rubbing half ring.

Images