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WO2017028195A1 - 低噪音汽车尾箱减速器 - Google Patents

低噪音汽车尾箱减速器 Download PDF

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Publication number
WO2017028195A1
WO2017028195A1 PCT/CN2015/087306 CN2015087306W WO2017028195A1 WO 2017028195 A1 WO2017028195 A1 WO 2017028195A1 CN 2015087306 W CN2015087306 W CN 2015087306W WO 2017028195 A1 WO2017028195 A1 WO 2017028195A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
planetary
stage
planetary gear
sun gear
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2015/087306
Other languages
English (en)
French (fr)
Inventor
李平
徐尚祥
任庆良
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Shenzhen Zhaowei Machinery and Electronics Co Ltd
Original Assignee
Shenzhen Zhaowei Machinery and Electronics Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Shenzhen Zhaowei Machinery and Electronics Co Ltd filed Critical Shenzhen Zhaowei Machinery and Electronics Co Ltd
Priority to JP2016561307A priority Critical patent/JP2017530303A/ja
Priority to PCT/CN2015/087306 priority patent/WO2017028195A1/zh
Priority to US15/127,961 priority patent/US20180172113A1/en
Priority to KR1020167026762A priority patent/KR101937006B1/ko
Priority to EP15885778.9A priority patent/EP3339681A4/en
Publication of WO2017028195A1 publication Critical patent/WO2017028195A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/0006—Vibration-damping or noise reducing means specially adapted for gearings
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05F—DEVICES FOR MOVING WINGS INTO OPEN OR CLOSED POSITION; CHECKS FOR WINGS; WING FITTINGS NOT OTHERWISE PROVIDED FOR, CONCERNED WITH THE FUNCTIONING OF THE WING
    • E05F3/00—Closers or openers with braking devices, e.g. checks; Construction of pneumatic or liquid braking devices
    • E05F3/22—Additional arrangements for closers, e.g. for holding the wing in opened or other position
    • E05F3/221—Mechanical power-locks, e.g. for holding the wing open or for free-moving zones
    • E05F3/222—Mechanical power-locks, e.g. for holding the wing open or for free-moving zones electrically operated
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/46—Systems consisting of a plurality of gear trains each with orbital gears, i.e. systems having three or more central gears
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05F—DEVICES FOR MOVING WINGS INTO OPEN OR CLOSED POSITION; CHECKS FOR WINGS; WING FITTINGS NOT OTHERWISE PROVIDED FOR, CONCERNED WITH THE FUNCTIONING OF THE WING
    • E05F15/00—Power-operated mechanisms for wings
    • E05F15/60—Power-operated mechanisms for wings using electrical actuators
    • E05F15/603—Power-operated mechanisms for wings using electrical actuators using rotary electromotors
    • E05F15/611—Power-operated mechanisms for wings using electrical actuators using rotary electromotors for swinging wings
    • E05F15/614—Power-operated mechanisms for wings using electrical actuators using rotary electromotors for swinging wings operated by meshing gear wheels, one of which being mounted at the wing pivot axis; operated by a motor acting directly on the wing pivot axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/30—Toothed gearings for conveying rotary motion with gears having orbital motion in which an orbital gear has an axis crossing the main axis of the gearing and has helical teeth or is a worm
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
    • F16H47/02—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
    • F16H47/04—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type the mechanical gearing being of the type with members having orbital motion
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05Y—INDEXING SCHEME ASSOCIATED WITH SUBCLASSES E05D AND E05F, RELATING TO CONSTRUCTION ELEMENTS, ELECTRIC CONTROL, POWER SUPPLY, POWER SIGNAL OR TRANSMISSION, USER INTERFACES, MOUNTING OR COUPLING, DETAILS, ACCESSORIES, AUXILIARY OPERATIONS NOT OTHERWISE PROVIDED FOR, APPLICATION THEREOF
    • E05Y2201/00—Constructional elements; Accessories therefor
    • E05Y2201/60—Suspension or transmission members; Accessories therefor
    • E05Y2201/622—Suspension or transmission members elements
    • E05Y2201/71—Toothed gearing
    • E05Y2201/72—Planetary gearing
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05Y—INDEXING SCHEME ASSOCIATED WITH SUBCLASSES E05D AND E05F, RELATING TO CONSTRUCTION ELEMENTS, ELECTRIC CONTROL, POWER SUPPLY, POWER SIGNAL OR TRANSMISSION, USER INTERFACES, MOUNTING OR COUPLING, DETAILS, ACCESSORIES, AUXILIARY OPERATIONS NOT OTHERWISE PROVIDED FOR, APPLICATION THEREOF
    • E05Y2900/00—Application of doors, windows, wings or fittings thereof
    • E05Y2900/50—Application of doors, windows, wings or fittings thereof for vehicles
    • E05Y2900/53—Type of wing
    • E05Y2900/546—Tailboards, tailgates or sideboards opening upwards
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H2001/2881—Toothed gearings for conveying rotary motion with gears having orbital motion comprising two axially spaced central gears, i.e. ring or sun gear, engaged by at least one common orbital gear wherein one of the central gears is forming the output
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/0006—Vibration-damping or noise reducing means specially adapted for gearings
    • F16H2057/0012—Vibration-damping or noise reducing means specially adapted for gearings for reducing drive line oscillations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H57/082—Planet carriers

Definitions

  • the present invention relates to the field of reducer technology, and more particularly to a low noise automobile tail box reducer.
  • the existing automobile tail box reducer mainly adopts a multi-stage spur gear planetary reduction mechanism. Although the spur gear is easy to process, its coincidence is low and the running balance is poor, resulting in a large noise of the planetary reducer.
  • some automobile tail box reducers adopt a combination structure of straight teeth and helical teeth, helical teeth and helical teeth, but because the inner tooth shell adopts a combined structure, the straight teeth and the helical teeth or the stages are inclined. The tooth part needs to be machined, resulting in a complicated overall structure of the reducer, high assembly precision, high manufacturing difficulty, high cost, and poor sealing performance of the same speed reducer.
  • An object of the present invention is to provide a low-noise automobile tail box reducer, which aims to solve the problem that the prior art planetary reducer has large noise, poor running balance, and complicated structure of the combined helical internal tooth housing, and high assembly precision. , manufacturing difficulties and poor sealing performance.
  • the technical solution of the present invention is to provide a ⁇ ⁇ noise automobile tail box reducer, including an inner tooth case, an input mechanism disposed in the inner tooth case, and at least two stages of planetary gears a transmission mechanism
  • the inner gear housing includes an inner gear housing body and a first helical gear integrally formed on the inner wall of the inner gear housing
  • the at least two-stage planetary gear transmission mechanism includes a primary planetary gear transmission mechanism and a secondary planetary gear transmission
  • the primary planetary gear transmission includes an integrally formed primary planetary cage and a primary planetary gear mounted on the primary planetary cage, the secondary planetary gear transmission including a combined secondary planet a retainer and a secondary planetary gear mounted on the secondary planetary cage
  • the input mechanism comprising a first stage sun gear fixed to an output shaft of an external motor, the first stage sun gear Having a second helical gear, the primary planetary gear having a third oblique mesh with the second helical tooth a third helical tooth meshing
  • the primary planetary cage comprises a first top plate placed in parallel, a first bottom plate, and a first connecting column connecting the first top plate and the first bottom plate, the first connecting column a plurality of, and spaced apart, the first stage sun gear is located at a center between the first top plate and the first bottom plate, the plurality of secondary planetary gears are plural, and each of the secondary planetary gears passes through A fixed shaft is fixed between the two adjacent first connecting columns.
  • the first top plate is provided with a first mounting hole
  • the first bottom plate is provided with a second mounting hole
  • the two ends of the first fixed shaft are respectively fixed by the interference fit
  • the first mounting hole and the second mounting hole are described.
  • the center of the upper end surface and the center of the lower end surface of the first-stage planetary gear are respectively provided with a sinking groove, and each of the sinking slots is provided with a gasket, and both ends of the first fixed shaft are respectively worn The gasket extends into the first mounting hole and the second mounting hole.
  • the spacer is in interference fit with the sinking groove, and the first fixed shaft and the spacer are matched with each other.
  • the secondary planetary cage comprises a second top plate placed in parallel, a second bottom plate, and a second connecting column connecting the second top plate and the second bottom plate, the second connecting column a plurality of, and spaced apart, the secondary sun gear is located at a center between the second top plate and the second bottom plate, the plurality of secondary planetary gears are plural, and each of the secondary planetary gears passes through The two fixed shafts are fixed between the two adjacent second connecting columns.
  • a top surface of the second top plate is provided with a hollow sleeve, and the sleeve is provided with an internal spline that can cooperate with an external output mechanism to output power, and the bottom of the sleeve is provided a plug, the bottom surface of the plug is in contact with a top surface of the secondary sun gear on the first-stage planetary cage.
  • one end of the inner tooth housing is provided with an output port, the sleeve is protruded from the outer tooth housing by the output port, and the sleeve is disposed between the sleeve and the output port Output bearing.
  • one end of the inner gear housing is provided with an output port, and the sleeve extends from the output port to the outside of the inner tooth housing, between the sleeve and the output port With output bearings.
  • the other end of the inner gear body is provided with an input port, and the input port is provided with an end cover, and the inner gear body and the end cover are fixedly connected by screws, and the external motor An output shaft is coupled to the primary sun gear through the end cap.
  • the helical tooth structure in the inner tooth shell is integrally formed with the inner tooth shell body, thereby avoiding the manufacturing error caused by the processing and reassembly of the meshing portion of the helical tooth and the gears of each stage, and the first-order planetary maintenance
  • the frame also adopts a monolithic structure, which simplifies the internal structure of the inner toothed casing, improves the overall running accuracy and sealing of the reducer, and avoids the assembly error caused by the combined assembly; moreover, the first-stage sun gear, the first-stage planetary gear, The two-stage sun gear, the two-stage planetary gear and the inner gear body are all driven by helical gears with high degree of coincidence, stable operation and large carrying capacity.
  • the above structure also makes the reducer structure more compact and more compact. Small. Brief description of the drawing
  • FIG. 1 is a side view of a low noise automobile tail box reducer according to an embodiment of the present invention
  • FIG. 2 is a cross-sectional view of a low noise automobile tail box reducer according to an embodiment of the present invention
  • FIG. 3 is a cross-sectional view of an inner tooth housing in an embodiment of the present invention.
  • FIG. 4 is an exploded perspective view of a low noise automobile tail box reducer according to an embodiment of the present invention.
  • FIG. 5 is an exploded perspective view of a primary planetary gear transmission mechanism according to an embodiment of the present invention.
  • FIG. 6 is an exploded perspective view of a secondary planetary cage provided by an embodiment of the present invention.
  • 31-stage planetary cage 311-first top plate; 312-first bottom plate;
  • a low noise automobile tail box reducer includes an inner tooth housing 10, an input mechanism 20 disposed in the inner gear housing 10, and at least two stages of planetary gear transmission mechanisms ( In this embodiment, it is a two-stage planetary gear transmission mechanism).
  • the inner housing 10 includes an inner housing body 11 and a first helical tooth 12 integrally formed on the inner wall of the inner housing body 11.
  • the two-stage planetary gear transmission mechanism includes a primary planetary gear transmission mechanism 30 and a secondary planetary gear transmission mechanism 40.
  • the primary planetary gear mechanism 30 includes an integrally formed primary planetary cage 31 and a primary planetary gear 32 mounted to the primary planetary cage 31.
  • the secondary planetary gear transmission 40 includes a combined secondary planetary cage 41 and a secondary planetary gear 42 mounted to the secondary planetary cage 41.
  • the input mechanism 20 includes a first stage sun gear 21, and the first stage sun gear 21 is fixed to the output shaft 51 of the external motor 50.
  • the fixed first stage sun gear 21 has a second helical gear 22, and the primary planetary gear 32 has a third helical tooth 321 that meshes with the second helical tooth 22, and the third helical tooth 321 and the first helical tooth 12 of the inner wall of the inner toothed casing 10 Engaging, the primary planetary cage 31 is provided with a secondary sun gear 43, the secondary sun gear 43 has a fourth helical gear 431, and the secondary planetary gear 42 has a fifth helical tooth 421 that meshes with the fourth helical tooth 431, The five helical teeth 421 mesh with the first helical teeth 12.
  • the helical tooth structure in the inner tooth housing 10 is integrally formed with the inner tooth housing body 11 to avoid helical teeth.
  • the manufacturing error caused by the machining and re-assembly of the gear meshing parts of each stage is also the same.
  • the first-stage planetary cage 31 also adopts a monolithic structure, which simplifies the internal structure of the internal gear housing 10 and improves the overall running accuracy of the reducer. And sealing performance, avoiding assembly error caused by combined assembly;
  • helical teeth are used between the first stage sun gear 21, the first stage planetary gear 32, the second stage sun gear 43, the secondary planetary gear 42 and the inner gear housing 11
  • the transmission has high degree of coincidence, stable operation and large carrying capacity.
  • the above structure also makes the reducer structure more compact and compact.
  • the primary planetary cage 31 includes a first top plate 311 placed in parallel, a first bottom plate 312, and a first connecting post 313 connecting the first top plate 311 and the first bottom plate 312.
  • the first top plate 311, the first bottom plate 312, and the first connecting post 313 are integrally formed.
  • This monolithic structure improves the relative accuracy of the first top plate 311 of the cage and the first bottom plate 312 without assembly errors.
  • the first connecting columns 313 are three and spaced apart. Thus, three accommodating spaces are formed between the three first connecting columns 313 for respectively placing the three primary planetary gears 32.
  • Each of the primary planetary gears 32 is fixed to the accommodating space between the adjacent two first connecting columns 313 by the first fixed shaft 33.
  • the first stage sun gear 21 is located at the center between the first top plate 311 and the first bottom plate 312, i.e., at the center of the three primary planetary gears 32.
  • the first stage sun gear 21 is rotated coaxially. Since the first stage sun gear 21 meshes with the three primary planetary gears 32, the first stage sun gear 21 drives three.
  • the first planetary gears 32 rotate in the opposite direction around the first fixed shaft 33.
  • the three primary planetary gears 32 mesh with the first helical teeth 12 of the inner gear housing 10, and the inner gear housing 10 is fixed, that is, the inner tooth housing 10 does not rotate, so that the three primary planetary gears 32 drive the first-stage planetary cage 31 to rotate, and the first-stage planetary cage 31 rotates in the same direction as the first-stage sun gear 21 to complete the first-stage deceleration.
  • the first top plate 311 is provided with a first mounting hole 314, and the first bottom plate 312 is provided with a second mounting hole 315.
  • the two ends of the first fixed shaft 33 are respectively fixed by the interference fit.
  • a mounting hole 314 and a second mounting hole 315 are included.
  • the primary planetary gear 32 is sleeved on the first fixed shaft 33. The interference fixing between the two ends of the first fixed shaft 33 makes the installation of the first fixed shaft 33 stronger, and further avoids the deformation of the primary planetary gear 32 under load or work, and improves the running stability of the reducer. .
  • the center of the upper end surface of the first-stage planetary gear 32 and the center of the lower end surface are respectively provided with a sinking groove 322, and each of the sinking grooves 322 is provided with a gasket 34, and both ends of the first fixed shaft 33 are respectively worn.
  • the spacer 34 extends into the first mounting hole 314 and the second mounting hole 315. After the primary planetary gear 32 is installed, the two spacers 34 are respectively Between the primary planetary gear 32 and the first top plate 311, and between the primary planetary gear 32 and the first bottom plate 312, the protection of the spacer 34 prevents the primary planetary cage 31 from being on the primary planetary gear 32. The end face and the lower end face are scratched, and on the other hand, the noise of the reducer is also reduced.
  • the spacer 34 has an interference fit with the sinker 322 through its outer diameter, and the first fixed shaft 33 passes through the spacer 34 ⁇ , and the first fixed shaft 33 and the inner hole of the spacer 34 are clearance-fitted. With this tolerance fit, the radial runout of the primary planetary gear 32 during installation and operation is avoided, reducing the difficulty of assembly.
  • the secondary planetary cage 41 includes a second top plate 411 placed in parallel, a second bottom plate 412, and a second connecting post 413 connecting the second top plate 411 and the second bottom plate 412.
  • the plurality of second connecting columns 413 are four (four in this embodiment) and are spaced apart.
  • the plurality of secondary planetary gears 42 are plural (four in this embodiment), and each of the secondary planetary gears 42 is fixed between the adjacent two second connecting columns 413 by the second fixed shaft 44.
  • the secondary sun gear 43 is located at the center between the second top plate 411 and the second bottom plate 412. It is located at the center of the four secondary planetary gears 42.
  • the top surface of the second top plate 411 is provided with a hollow sleeve 414, and the sleeve 414 is provided with an internal spline 415 that can cooperate with an external output mechanism to output power, and the bottom of the sleeve 414 is provided.
  • the plug 416 has a bottom surface that is in contact with the top surface of the secondary sun gear 43 on the primary planetary cage 31. Since in this embodiment, only the secondary planetary gear mechanism is provided, the internal spline 415 is provided as an output end on the secondary planetary cage 41 to cooperate with the external output mechanism to output power outward.
  • an internal spline 415 is provided as an output on the last stage of the planetary cage.
  • a plug 416 is provided, on the one hand, the bottom of the sleeve 414 is blocked to prevent foreign matter from falling into the inner toothed casing 10 by the sleeve 414.
  • the plug 416 is axially aligned with the first-stage planetary cage 31.
  • the secondary sun gear 43 performs the limit position, reduces the axial runout, and improves the running stability of the reducer.
  • one end of the inner gear housing 11 is provided with an output port 111.
  • the sleeve 414 protrudes from the outer housing body 11 through the output port 111, and an output bearing 417 is disposed between the sleeve 414 and the output port 111.
  • the output bearing 417 is provided here to reduce the sliding friction between the sleeve 414 and the inner wall of the inner housing body 11, thereby also reducing noise.
  • FIG. 4 the other end of the inner gear housing 11 is provided with an input port 112, and the input port 112 is provided with an end cover 52.
  • the inner tooth housing 10 and the end cover 52 are fixedly connected by screws,
  • the output shaft 51 of the external motor 50 is connected to the first stage sun gear 21 through the end cover 52.
  • the inner tooth housing 10 and the end cover 52 employ such a connection structure to improve the sealing level of the inner housing 10.
  • an input bearing 53 is provided between the output shaft 51 of the external motor 50 and the primary planetary holder 31. Set the input bearing 53, support the output shaft 51 of the external motor 50, and improve its rotation accuracy.
  • the structure of the integral inner tooth housing 10 and the structure of the integral first-class planetary cage 31 are adopted, which simplifies the structure of the inner tooth housing 10, improves the assembly precision of the reducer, and improves the planetary
  • the smooth running of the gear reduces the noise of the reducer and improves the load carrying capacity.

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  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)
  • General Details Of Gearings (AREA)

Abstract

一种低噪音汽车尾箱减速器，包括内齿壳(10)、输入机构(20)及至少两级行星齿轮传动机构(30、40)，内齿壳(10)包括内齿壳本体(11)以及一体成型于内齿壳本体(11)内壁的第一斜齿(12)，一级行星齿轮传动机构(30)中的一级行星保持架(31)一体成型，输入机构(20)包括一级太阳轮(21)；一级太阳轮(21)、一级行星齿轮(32)、二级太阳轮(43)、二级行星齿轮(42)及内齿壳本体(11)之间均采用斜齿传动。所述低噪音汽车尾箱减速器中，斜齿结构与内齿壳本体一体成型，可避免斜齿分别加工而带来的制造误差，同时一级行星保持架也采用整体式结构，可提高减速器整体的运行精度和密封性能，避免组合装配带来的装配误差；各传动轮之间均采用斜齿传动，重合度高，运行平稳，承载能力大。

Description

氐噪音汽车尾箱减速器
技术领域
[0001] 本发明涉及减速器技术领域， 更具体地说， 是涉及一种低噪音汽车尾箱减速器 背景技术
[0002] 现有的汽车尾箱减速器主要采用多级直齿齿轮行星减速机构。 直齿齿轮虽然加 工方便， 但其重合度低， 运行平衡性较差， 导致行星减速器噪音较大。 为改善 噪音问题， 部分汽车尾箱减速器采用了直齿与斜齿、 斜齿与斜齿的组合式结构 ， 但由于内齿壳采用组合式结构， 使得直齿与斜齿部分或各级斜齿部分需要分 幵加工， 导致减速器整体结构复杂， 装配精度要求高， 制造难度大， 成本较高 ， 同吋减速器的密封性能较差。
技术问题
[0003] 本发明的目的在于提供一种低噪音汽车尾箱减速器， 旨在解决现有技术中行星 减速器噪音大、 运行平衡性差以及组合式斜齿内齿壳结构复杂、 装配精度要求 高、 制造难度大以及密封性能差的问题。
问题的解决方案
技术解决方案
[0004] 为解决上述技术问题， 本发明的技术方案是： 提供一种 ί氐噪音汽车尾箱减速 器， 包括内齿壳、 设于所述内齿壳内的输入机构及至少两级行星齿轮传动机构 , 所述内齿壳包括内齿壳本体以及一体成型于所述内齿壳本体内壁的第一斜齿 , 至少两级行星齿轮传动机构包括一级行星齿轮传动机构及二级行星齿轮传动 机构， 所述一级行星齿轮传动机构包括一体成型的一级行星保持架以及安装于 所述一级行星保持架上的一级行星齿轮， 所述二级行星齿轮传动机构包括组合 式二级行星保持架以及安装于所述二级行星保持架上的二级行星齿轮， 所述输 入机构包括一级太阳轮， 所述一级太阳轮固定于外部电机的输出轴上， 所述一 级太阳轮具有第二斜齿， 所述一级行星齿轮具有与所述第二斜齿啮合的第三斜 齿， 第三斜齿与所述第一斜齿啮合， 所述一级行星保持架上设有二级太阳轮， 所述二级太阳轮具有第四斜齿， 所述二级行星齿轮具有与所述第四斜齿啮合的 第五斜齿， 所述第五斜齿与所述第一斜齿啮合。
[0005] 可选地， 所述一级行星保持架包括平行放置的第一顶板、 第一底板以及连接所 述第一顶板与所述第一底板的第一连接柱， 所述第一连接柱为多个， 且间隔设 置， 所述一级太阳轮位于所述第一顶板与所述第一底板之间的中心， 所述二级 行星齿轮为多个， 且每个二级行星齿轮通过第一固定轴固定于相邻两所述第一 连接柱之间。
[0006] 可选地， 所述第一顶板上设有第一安装孔， 所述第一底板上设有第二安装孔， 所述第一固定轴的两端分别通过过盈配合固定于所述第一安装孔与所述第二安 装孔内。
[0007] 可选地， 所述一级行星齿轮的上端面中心与下端面中心分别设有沉槽， 各所述 沉槽内均设有垫片， 所述第一固定轴的两端分别穿过所述垫片伸入所述第一安 装孔与所述第二安装孔内。
[0008] 可选地， 所述垫片与所述沉槽过盈配合， 所述第一固定轴与所述垫片之间间隙 配合。
[0009] 可选地， 所述二级行星保持架包括平行放置的第二顶板、 第二底板以及连接所 述第二顶板与所述第二底板的第二连接柱， 所述第二连接柱为多个， 且间隔设 置， 所述二级太阳轮位于所述第二顶板与所述第二底板之间的中心， 所述二级 行星齿轮为多个， 且每个二级行星齿轮通过第二固定轴固定于相邻两所述第二 连接柱之间。
[0010] 可选地， 所述第二顶板的顶面设有中空的套筒， 所述套筒设有可与外部输出机 构配合以将动力输出的内花键， 所述套筒底部设有堵头， 所述堵头底面与所述 一级行星保持架上的二级太阳轮的顶面触接。
[0011] 可选地， 所述内齿壳的一端设有输出口， 所述套筒由所述输出口伸出所述内齿 壳外， 所述套筒与所述输出口之间设有输出轴承。
[0012] 可选地， 所述内齿壳本体的一端设有输出口， 所述套筒由所述输出口伸出所述 内齿壳本体外， 所述套筒与所述输出口之间设有输出轴承。 [0013] 可选地， 所述内齿壳本体的另一端设有输入口， 所述输入口处设有端盖， 所述 内齿壳本体与所述端盖通过螺钉固定连接， 外部电机的输出轴穿过所述端盖与 所述一级太阳轮连接。
发明的有益效果
有益效果
[0014] 本发明中， 内齿壳内的斜齿结构与内齿壳本体一体成型， 避免斜齿与各级齿轮 啮合部分分别加工再装配而带来的制造误差， 同吋， 一级行星保持架也采用整 体式结构， 同吋简化了内齿壳内部结构， 提高减速器整体的运行精度和密封性 育 ， 避免组合装配带来的装配误差； 而且， 一级太阳轮、 一级行星齿轮、 二级 太阳轮、 二级行星齿轮及内齿壳本体之间均采用斜齿传动， 重合度高， 运行平 稳， 承载能力大； 同吋， 上述这种结构也使减速器结构更紧凑， 体积更小巧。 对附图的简要说明
附图说明
[0015] 图 1是本发明实施例提供的低噪音汽车尾箱减速器的侧视图；
[0016] 图 2是本发明实施例提供的低噪音汽车尾箱减速器的剖视图；
[0017] 图 3是本发明实施例中内齿壳的剖视图；
[0018] 图 4是本发明实施例提供的低噪音汽车尾箱减速器的分解示意图；
[0019] 图 5是本发明实施例提供的一级行星齿轮传动机构的分解示意图；
[0020] 图 6是本发明实施例提供的二级行星保持架的分解示意图；
[0021] 10-内齿壳； 11-内齿壳本体； 111-输出口；
[0022] 112-输入口； 12-第一斜齿； 20-输入机构；
[0023] 21-—级太阳轮； 22-第二斜齿； 30-—级行星齿轮传动机构；
[0024] 31-—级行星保持架； 311-第一顶板； 312-第一底板；
[0025] 313-第一连接柱； 314-第一安装孔； 315-第二安装孔；
[0026] 32-—级行星齿轮； 321-第三斜齿； 322-沉槽；
[0027] 33-第一固定轴； 34-垫片； 40-二级行星齿轮传动机构；
[0028] 41-二级行星保持架； 411-第二顶板； 412-第二底板；
[0029] 413-第二连接柱； 414-套筒； 415-内花键； [0030] 416-堵头； 417-输出轴承； 42-二级行星齿轮；
[0031] 421-第五斜齿； 43-二级太阳轮； 431-第四斜齿；
[0032] 44-第二固定轴； 50-外部电机； 51-输出轴；
[0033] 52-端盖； 53-输入轴承。
本发明的实施方式
[0034] 为了使本发明的目的、 技术方案及优点更加清楚明白， 以下结合附图及实施例 ， 对本发明进行进一步详细说明。 应当理解， 此处所描述的具体实施例仅仅用 以解释本发明， 并不用于限定本发明。
[0035] 需要说明的是， 当元件被称为 "固定于"或"设置于"另一个元件， 它可以直接在 另一个元件上或者可能同吋存在居中元件。 当一个元件被称为"连接于 "另一个元 件， 它可以是直接连接到另一个元件或者可能同吋存在居中元件。
[0036] 还需要说明的是， 本实施例中的左、 右、 上、 下等方位用语， 仅是互为相对概 念或是以产品的正常使用状态为参考的， 而不应该认为是具有限制性的。
[0037] 参照图 1至图 3， 本发明实施例提供的低噪音汽车尾箱减速器， 包括内齿壳 10、 设于内齿壳 10内的输入机构 20及至少两级行星齿轮传动机构 （本实施例中为两 级行星齿轮传动机构） 。 内齿壳 10包括内齿壳本体 11以及一体成型于内齿壳本 体 11内壁的第一斜齿 12。 而两级行星齿轮传动机构包括一级行星齿轮传动机构 3 0及二级行星齿轮传动机构 40。 一级行星齿轮传动机构 30包括一体成型的一级行 星保持架 31以及安装于一级行星保持架 31上的一级行星齿轮 32。 二级行星齿轮 传动机构 40包括组合式二级行星保持架 41以及安装于二级行星保持架 41上的二 级行星齿轮 42。 输入机构 20包括一级太阳轮 21， 一级太阳轮 21固定于外部电机 5 0的输出轴 51上。 固定一级太阳轮 21具有第二斜齿 22， 一级行星齿轮 32具有与第 二斜齿 22啮合的第三斜齿 321， 第三斜齿 321与内齿壳 10内壁的第一斜齿 12啮合 ， 一级行星保持架 31上设有二级太阳轮 43， 二级太阳轮 43具有第四斜齿 431， 二 级行星齿轮 42具有与第四斜齿 431啮合的第五斜齿 421， 第五斜齿 421与第一斜齿 12啮合。
[0038] 本发明实施例中， 内齿壳 10内的斜齿结构与内齿壳本体 11一体成型， 避免斜齿 与各级齿轮啮合部分分别加工再装配而带来的制造误差， 同吋， 一级行星保持 架 31也采用整体式结构， 同吋简化了内齿壳 10内部结构， 提高减速器整体的运 行精度和密封性能， 避免组合装配带来的装配误差； 而且， 一级太阳轮 21、 一 级行星齿轮 32、 二级太阳轮 43、 二级行星齿轮 42及内齿壳本体 11之间均采用斜 齿传动， 重合度高， 运行平稳， 承载能力大； 同吋， 上述这种结构也使减速器 结构更紧凑， 体积更小巧。
[0039] 参照图 4、 图 5， 一级行星保持架 31包括平行放置的第一顶板 311、 第一底板 312 以及连接第一顶板 311与第一底板 312的第一连接柱 313。 第一顶板 311、 第一底 板 312以及第一连接柱 313—体成型。 这种整体式结构， 提高保持架第一顶板 311 与第一底板 312的相对精度， 不会出现装配误差。 由图所示， 第一连接柱 313为 三个， 且间隔设置。 这样， 三个第一连接柱 313之间形成三个容置空间分别用来 放置三个一级行星齿轮 32。 每个一级行星齿轮 32通过第一固定轴 33固定于相邻 两第一连接柱 313之间的容置空间内。 一级太阳轮 21位于第一顶板 311与第一底 板 312之间的中心， 即位于三个一级行星齿轮 32的中心。
[0040] 当外部电机 50的输出轴 51转动吋， 带动一级太阳轮 21同轴转动， 由于一级太阳 轮 21与三个一级行星齿轮 32相啮合， 则一级太阳轮 21驱动三个一级行星齿轮 32 反方向绕第一固定轴 33转动， 同吋， 三个一级行星齿轮 32又与内齿壳 10的第一 斜齿 12啮合， 而内齿壳 10固定， 即内齿壳 10不转动， 这样， 就使得三个一级行 星齿轮 32带动一级行星保持架 31转动， 一级行星保持架 31转动方向与一级太阳 轮 21转动方向相同， 完成一级减速。
[0041] 本实施例中， 第一顶板 311上设有第一安装孔 314， 第一底板 312上设有第二安 装孔 315， 第一固定轴 33的两端分别通过过盈配合固定于第一安装孔 314与第二 安装孔 315内。 而一级行星齿轮 32套于第一固定轴 33上。 而第一固定轴 33两端采 用过盈配合， 使第一固定轴 33的安装更牢固， 也进一步地避免一级行星齿轮 32 在承受负载或工作吋的变形， 提高了减速器的运行平稳性。
[0042] 作为进一步优化方案， 一级行星齿轮 32的上端面中心与下端面中心分别设有沉 槽 322， 各沉槽 322内均设有垫片 34， 第一固定轴 33的两端分别穿过垫片 34伸入 第一安装孔 314与第二安装孔 315内。 一级行星齿轮 32在安装后， 两垫片 34分别 位于一级行星齿轮 32与第一顶板 311， 以及一级行星齿轮 32与第一底板 312之间 ， 通过垫片 34的保护作用， 不仅避免一级行星保持架 31被一级行星齿轮 32的上 端面及下端面划伤， 另一方面， 也降低了减速器的噪音。
[0043] 进一步地， 垫片 34通过其外径与沉槽 322过盈配合， 第一固定轴 33穿过垫片 34 吋， 第一固定轴 33与垫片 34的内孔之间间隙配合。 采用这种公差配合方式， 避 免一级行星齿轮 32在安装和运行过程中的径向跳动， 降低装配的难度。
[0044] 结合图 4、 图 6， 二级行星保持架 41包括平行放置的第二顶板 411、 第二底板 412 以及连接第二顶板 411与第二底板 412的第二连接柱 413。 第二连接柱 413为多个 (本实施例为四个） ， 且间隔设置。 二级行星齿轮 42为多个 （本实施例为四个 ) ， 且每个二级行星齿轮 42通过第二固定轴 44固定于相邻两第二连接柱 413之间 。 二级太阳轮 43位于第二顶板 411与第二底板 412之间的中心。 即位于四个二级 行星齿轮 42的中心。
[0045] 当一级行星保持架 31转动吋， 其上的二级太阳轮 43也发生转动， 由于二级太阳 轮 43与四个二级行星齿轮 42啮合， 则二级太阳轮 43驱动四个二级行星齿轮 42反 方向绕第二固定轴 33转动， 同吋， 四个二级行星齿轮 42又与内齿壳 10的第一斜 齿 12啮合， 同样由于内齿壳 10固定， 即内齿壳 10不转动， 这样， 就使得四个二 级行星齿轮 42带动二级行星保持架 41转动， 二级行星保持架 41转动方向与二级 太阳轮 43转动方向相同， 完成二级减速。
[0046] 本实施例中， 第二顶板 411的顶面设有中空的套筒 414， 套筒 414设有可与外部 输出机构配合以将动力输出的内花键 415， 套筒 414底部设有堵头 416， 堵头 416 底面与一级行星保持架 31上的二级太阳轮 43的顶面触接。 由于本实施例中， 只 有二级行星齿轮机构， 所以在二级行星保持架 41上设置内花键 415作为输出端， 与外部输出机构配合， 向外输出动力。 当然， 如果有更多级行星齿轮机构吋， 在最后一级的行星保持架上设置内花键 415作为输出端即可。 此处设置堵头 416 ， 一方面对套筒 414底部进行封堵， 避免异物由套筒 414落入内齿壳 10内， 同吋 ， 堵头 416在轴向上对一级行星保持架 31上的二级太阳轮 43进行限位， 降低轴向 跳动， 提高减速器的运行平稳性。
[0047] 当二级行星保护架 41转动吋， 套筒 414随之转动， 同吋， 套筒 414通过内花键 41 5带动输出机构转动， 从而将动力输出。
[0048] 进一步地， 内齿壳本体 11的一端设有输出口 111， 套筒 414由输出口 111伸出内 齿壳本体 11外， 套筒 414与输出口 111之间设有输出轴承 417。 此处设置输出轴承 417， 减小了套筒 414与内齿壳本体 11内壁之间的滑动摩擦， 从而也降低了噪音
[0049] 结合图 2、 图 4， 内齿壳本体 11的另一端设有输入口 112， 输入口 112处设有端盖 52， 内齿壳 10与端盖 52通过螺钉固定连接， 同吋， 外部电机 50的输出轴 51穿过 端盖 52与一级太阳轮 21连接。 内齿壳 10与端盖 52采用这种连接结构， 提高内齿 壳 10的密封等级。
[0050] 同样的， 外部电机 50的输出轴 51与一级行星保持架 31之间设有输入轴承 53。 设 置输入轴承 53， 对外部电机 50的输出轴 51起到支撑作用， 同吋提高其回转精度
[0051] 综上， 本发明实施例中， 采用了整体式内齿壳 10结构以及整体式一级行星保持 架 31结构， 简化了内齿壳 10结构， 提高了减速器装配精度， 提高了行星齿轮的 运行平稳性， 降低了减速器的噪音， 提高了承载能力。
[0052] 以上仅为本发明的较佳实施例而已， 并不用以限制本发明， 凡在本发明的精神 和原则之内所作的任何修改、 等同替换和改进等， 均应包含在本发明的保护范 围之内。

Claims

权利要求书
[权利要求 1] 一种低噪音汽车尾箱减速器， 包括内齿壳、 设于所述内齿壳内的输入 机构及至少两级行星齿轮传动机构， 其特征在于： 所述内齿壳包括内 齿壳本体以及一体成型于所述内齿壳本体内壁的第一斜齿， 至少两级 行星齿轮传动机构包括一级行星齿轮传动机构及二级行星齿轮传动机 构， 所述一级行星齿轮传动机构包括一体成型的一级行星保持架以及 安装于所述一级行星保持架上的一级行星齿轮， 所述二级行星齿轮传 动机构包括组合式二级行星保持架以及安装于所述二级行星保持架上 的二级行星齿轮， 所述输入机构包括一级太阳轮， 所述一级太阳轮固 定于外部电机的输出轴上， 所述一级太阳轮具有第二斜齿， 所述一级 行星齿轮具有与所述第二斜齿啮合的第三斜齿， 第三斜齿与所述第一 斜齿啮合， 所述一级行星保持架上设有二级太阳轮， 所述二级太阳轮 具有第四斜齿， 所述二级行星齿轮具有与所述第四斜齿啮合的第五斜 齿， 所述第五斜齿与所述第一斜齿啮合。
[权利要求 2] 如权利要求 1所述的低噪音汽车尾箱减速器， 其特征在于： 所述一级 行星保持架包括平行放置的第一顶板、 第一底板以及连接所述第一顶 板与所述第一底板的第一连接柱， 所述第一连接柱为多个， 且间隔设 置， 所述一级太阳轮位于所述第一顶板与所述第一底板之间的中心， 所述二级行星齿轮为多个， 且每个二级行星齿轮通过第一固定轴固定 于相邻两所述第一连接柱之间。
[权利要求 3] 如权利要求 2所述的低噪音汽车尾箱减速器， 其特征在于： 所述第一 顶板上设有第一安装孔， 所述第一底板上设有第二安装孔， 所述第一 固定轴的两端分别通过过盈配合固定于所述第一安装孔与所述第二安 装孔内。
[权利要求 4] 如权利要求 3所述的低噪音汽车尾箱减速器， 其特征在于： 所述一级 行星齿轮的上端面中心与下端面中心分别设有沉槽， 各所述沉槽内均 设有垫片， 所述第一固定轴的两端分别穿过所述垫片伸入所述第一安 装孔与所述第二安装孔内。 如权利要求 4所述的低噪音汽车尾箱减速器， 其特征在于： 所述垫片 与所述沉槽过盈配合， 所述第一固定轴与所述垫片之间间隙配合。 如权利要求 1至 5中任一项所述的低噪音汽车尾箱减速器， 其特征在于 ： 所述二级行星保持架包括平行放置的第二顶板、 第二底板以及连接 所述第二顶板与所述第二底板的第二连接柱， 所述第二连接柱为多个 ， 且间隔设置， 所述二级太阳轮位于所述第二顶板与所述第二底板之 间的中心， 所述二级行星齿轮为多个， 且每个二级行星齿轮通过第二 固定轴固定于相邻两所述第二连接柱之间。
如权利要求 6所述的低噪音汽车尾箱减速器， 其特征在于： 所述第二 顶板的顶面设有中空的套筒， 所述套筒设有可与外部输出机构配合以 将动力输出的内花键， 所述套筒底部设有堵头， 所述堵头底面与所述 一级行星保持架上的二级太阳轮的顶面触接。
如权利要求 6所述的低噪音汽车尾箱减速器， 其特征在于： 所述内齿 壳本体的一端设有输出口， 所述套筒由所述输出口伸出所述内齿壳本 体外， 所述套筒与所述输出口之间设有输出轴承。
如权利要求 1至 5中任一项所述的低噪音汽车尾箱减速器， 其特征在于 ： 所述内齿壳本体的另一端设有输入口， 所述输入口处设有端盖， 所 述内齿壳本体与所述端盖通过螺钉固定连接， 外部电机的输出轴穿过 所述端盖与所述一级太阳轮连接。
如权利要求 9所述的低噪音汽车尾箱减速器， 其特征在于： 外部电机 的输出轴与所述一级行星保持架之间设有输入轴承。
PCT/CN2015/087306 2015-08-18 2015-08-18 低噪音汽车尾箱减速器 Ceased WO2017028195A1 (zh)

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US15/127,961 US20180172113A1 (en) 2015-08-18 2015-08-18 Low-noise car trunk reducer
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