CN213870961U

CN213870961U - Back clearance self-adaptive adjustment planetary transmission mechanism and speed reducer

Info

Publication number: CN213870961U
Application number: CN202021853934.7U
Authority: CN
Inventors: 李汉江
Original assignee: Shenzhen Qichilong Technology Co ltd
Current assignee: Shenzhen Qichilong Technology Co ltd
Priority date: 2020-08-28
Filing date: 2020-08-28
Publication date: 2021-08-03
Anticipated expiration: 2030-08-28

Abstract

The utility model discloses a back clearance self-adaptive adjustment planetary transmission mechanism and a speed reducer; the back clearance self-adaptive adjustment planetary transmission mechanism comprises a driving mechanism, a primary transmission system, an output shaft and a fixed supporting piece; the primary transmission system comprises a primary sun gear, a primary planet gear, a primary inner gear ring and a primary planet carrier; the first-stage planet carrier comprises a first-stage rotating arm and a first-stage planet disc; the first-stage rotating arm is elastically connected with the first-stage planetary plate through a first elastic piece; the first-stage planetary disc is in transmission connection with an output shaft, and the output shaft is rotatably connected in the fixed supporting piece; the speed reducer comprises a speed reducer box body and a back clearance self-adaptive adjusting planetary transmission mechanism, the fixed support piece is arranged on the speed reducer box body, and the back clearance self-adaptive adjusting planetary transmission mechanism is arranged in the speed reducer box body. The utility model discloses a back clearance self-adaptation regulation planetary transmission mechanism and speed reducer can eliminate the back clearance in the planet speed reduction transmission to self-adaptation regulation is with compensation wearing and tearing when can taking place wearing and tearing between the gear, guarantees the transmission precision.

Description

Back clearance self-adaptive adjustment planetary transmission mechanism and speed reducer

Technical Field

The utility model relates to a speed reduction drive technical field especially relates to a back clearance self-adaptation regulation planetary drive mechanism and speed reducer.

Background

The planetary speed reducing motor is widely applied to various industries due to the advantages of compact structure, large speed reducing ratio and the like, however, with the development of production technology and the requirement of high-quality products, particularly the development requirement of precise heavy-load transmission, higher requirements are provided for the transmission precision of the planetary speed reducing motor. The transmission precision of the planetary reducer is closely related to the return clearance of the planetary reducer, and the return clearance of the planetary reducer refers to: the input end of the speed reducer is fixed, so that the output end rotates clockwise and anticlockwise, and when the output end bears positive and negative rated torques, the angular displacement of the output end of the speed reducer is the return clearance, which is also called back clearance.

In the existing planetary reduction planetary transmission mechanism, in order to realize anti-backlash transmission (reduce or eliminate backlash), the common technical scheme is as follows: the method comprises an eccentric shaft sleeve center distance adjusting method, a double-piece thin gear staggered tooth adjusting method and a double-motor driven double-transmission chain gap eliminating method, and the methods have the problems of complex structure and assembly, high cost and the like. In addition, with the use of the planetary reducer, the abrasion among all gears of the planetary reducer is increased, so that the backlash is further increased, and the transmission efficiency is seriously influenced.

SUMMERY OF THE UTILITY MODEL

In order to overcome the not enough of prior art, one of the purposes of the utility model aims at providing a back clearance self-adaptation regulation planetary transmission mechanism, the utility model aims at providing a speed reducer, its back clearance that can eliminate in the planetary reduction transmission to self-adaptation regulation is with compensation wearing and tearing when can taking place wearing and tearing between the gear, guarantees transmission precision.

The utility model discloses an one of the purpose adopts following technical scheme to realize:

a backlash adaptive adjustment planetary transmission comprising: the driving mechanism, the primary transmission system, the output shaft and the fixed support piece; the primary transmission system comprises primary sun gears, primary planet gears, a primary inner gear ring and a primary planet carrier; the rotating shaft of the driving mechanism can be axially adjusted, and the primary sun gear and the rotating shaft of the driving mechanism are coaxially arranged and fixedly connected; the primary inner gear ring is fixedly arranged, and the primary planet gears are respectively meshed with the primary sun gear and the primary inner gear ring; the first-stage planet carrier comprises a first-stage rotating arm and a first-stage planet disc; the first-stage rotating arm is rotatably connected to a shaft hole of the first-stage planetary gear, and the first-stage rotating arm is elastically connected with the first-stage planetary disk through a first elastic piece; the first elastic part is suitable for applying force to the primary rotating arm along the axial direction of the primary planet gear so that the primary planet gear tends to approach the primary inner gear ring; the first-stage planetary disc is in transmission connection with the output shaft, the output shaft is rotatably connected in the fixed supporting piece, and the fixed supporting piece is suitable for providing radial supporting force for the output shaft.

Furthermore, the diameters of the root circles and the addendum circles of the primary sun gear, the primary planet gear and the primary inner gear ring are not changed, and the tooth thicknesses of the primary sun gear, the primary planet gear and the primary inner gear ring are suitable for linear change along the respective axial directions.

Furthermore, a secondary transmission system is arranged between the primary planetary disc and the output shaft, and comprises a secondary sun gear, a secondary planet gear, a secondary inner gear ring and a secondary planet carrier; the secondary sun gear is coaxially arranged with the primary planetary disk and is in transmission connection with the primary planetary disk; the secondary inner gear ring is fixedly arranged, and the secondary planet gear is respectively meshed with the secondary sun gear and the secondary inner gear ring; the secondary planet carrier comprises a secondary rotating arm and a secondary planet disc; the second-stage rotating arm is rotatably connected to a shaft hole of the second-stage planetary gear, and the second-stage rotating arm is elastically connected with the second-stage planetary disk through a second elastic piece; the second elastic part is suitable for applying force to the secondary rotating arm along the axial direction of the secondary planet teeth so that the secondary planet teeth have the tendency of approaching to the secondary inner gear ring; and the secondary planetary disk is in transmission connection with the output shaft.

Further, the elastic force of the second elastic member is greater than the elastic force of the first elastic member.

Further, the diameters of the root circle and the addendum circle of the secondary sun gear, the secondary planet gear and the secondary inner gear ring are not changed, and the tooth thicknesses of the secondary sun gear, the secondary planet gear and the secondary inner gear ring are suitable for linear change along the respective axial directions.

Furthermore, the rotating shaft and the output shaft of the driving mechanism are hollow shafts, and through holes are formed in the centers of the first-stage planetary disk and the second-stage planetary disk.

Furthermore, a ball bearing is arranged between the primary rotating arm and the shaft hole of the primary planet gear; the inner ring of the ball bearing is in interference fit with the first-stage rotating arm; and the outer ring of the ball bearing is in interference fit with the shaft hole of the primary planet gear.

A backlash adaptive adjustment planetary transmission comprising: the planetary gear type planetary gear set comprises a driving mechanism, a primary sun gear, a duplex planet gear, a first movable inner gear ring, a fixed planet carrier, a secondary sun gear, a secondary planet gear, a secondary inner gear ring, a secondary planet carrier, an output shaft and a fixed support piece; the rotating shaft of the driving mechanism can be axially adjusted, and the primary sun gear and the rotating shaft of the driving mechanism are coaxially arranged and fixedly connected; the first end of the duplex planet gear is meshed with the first-stage sun gear, and the second end of the duplex planet gear is meshed with the inner gear of the first movable inner gear ring; the fixed planet carrier comprises a fixed rotating arm and a fixed planet disk; the first movable inner gear ring comprises a first movable meshing part and a first movable connecting part; the fixed rotating arm is rotatably connected with the shaft hole of the duplex planet gear; the fixed rotating arm is elastically connected with the fixed planetary plate through a first elastic part and/or the first movable meshing part is connected with the first movable connecting part through a third elastic part; the first elastic member is adapted to apply a force to the fixed boom in an axial direction of the duplex planetary gear such that the second end of the duplex planetary gear has a tendency to approach the first movable ring gear; the third elastic member is adapted to apply a force to the first movable meshing portion in an axial direction of the double planetary gear so that the first movable meshing portion has a tendency to approach the second ends of the double planetary gears; the second-stage sun gear is coaxially arranged with the first movable connecting part and is in transmission connection with the first movable connecting part; the secondary inner gear ring is fixedly arranged, and the secondary planet gear is respectively meshed with the secondary sun gear and the secondary inner gear ring; the secondary planet carrier comprises a secondary rotating arm and a secondary planet disc; the second-stage rotating arm is rotatably connected to a shaft hole of the second-stage planetary gear, and the second-stage rotating arm is elastically connected with the second-stage planetary disk through a second elastic piece; the second elastic part is suitable for applying force to the secondary rotating arm along the axial direction of the secondary planet teeth so that the secondary planet teeth have the tendency of approaching to the secondary inner gear ring; the secondary planetary disc is in transmission connection with the output shaft, the output shaft is rotatably connected in the fixed support part, and the fixed support part is suitable for providing radial supporting force for the output shaft; the elasticity of the second elastic member is greater than the elasticity of the third elastic member and the elasticity of the first elastic member.

A backlash adaptive adjustment planetary transmission comprising: the driving mechanism, the primary sun gear, the duplex planet gear, the fixed inner gear ring, the movable planet carrier, the second movable inner gear ring, the output shaft and the fixed support piece; the rotating shaft of the driving mechanism can be axially adjusted, and the primary sun gear and the rotating shaft of the driving mechanism are coaxially arranged and fixedly connected; the first ends of the duplex planet gears are respectively meshed with the primary sun gear and the fixed inner gear ring, and the second ends of the duplex planet gears are meshed with the second movable inner gear ring; the movable planet carrier is rotatably connected with the double planetary gears; the fixed annular gear comprises a fixed meshing part and a fixed connecting part; the second movable inner gear ring comprises a second movable meshing part and a second movable connecting part; the fixed engaging part is elastically connected with the fixed connecting part through a fourth elastic part and/or the second movable engaging part is connected with the second movable connecting part through a third elastic part; the fourth elastic element is suitable for applying force to the duplex planet gears along the axial direction of the duplex planet gear teeth so that the second ends of the duplex planet gears have the tendency of approaching the second movable inner gear ring; the third elastic member is adapted to apply a force to the second movable meshing portion in an axial direction of the double planetary gear so that the second movable meshing portion has a tendency to approach the second ends of the double planetary gears; the second movable connecting part is in transmission connection with the output shaft, the output shaft is rotatably connected in the fixed supporting part, and the fixed supporting part is suitable for providing radial supporting force for the output shaft.

The second purpose of the utility model is realized by adopting the following technical scheme:

a speed reducer comprises a speed reducing box body and a back clearance self-adaptive adjusting planetary transmission mechanism, wherein the back clearance self-adaptive adjusting planetary transmission mechanism is installed in the speed reducing box body.

Compared with the prior art, the beneficial effects of the utility model reside in that: the rotating shaft of the driving mechanism can be axially adjusted, so that the axial position of the primary sun gear can be adjusted, and the running clearance between the primary sun gear and the planet gear or the duplex planet gear can be eliminated by adjusting the axial position of the primary sun gear, thereby ensuring the transmission precision; and the setting of first elastic component, second elastic component, third elastic component and fourth elastic component can provide the pretightning force between the gear for intermeshing to when taking place wearing and tearing to produce the clearance between the gear of intermeshing, each elastic component can the automatic adjustment produce the axial position between the meshing gear in clearance under the effect of elastic force, make its meshing inseparabler, reduced gear drive's back clearance, guaranteed the transmission precision.

Drawings

FIG. 1 is a schematic diagram of a first embodiment of a backlash self-adaptive adjusting planetary transmission according to the present invention;

FIG. 2 is a schematic block diagram of the addition of the two-stage powertrain of FIG. 1;

FIG. 3 is a schematic diagram of the driving mechanism in FIG. 2, in which the rotating shaft and the output shaft are hollow shafts, the centers of the first-stage planetary disk and the second-stage planetary disk are through holes;

FIG. 4 is a schematic diagram of a second embodiment of the self-adaptive back lash adjustment planetary transmission of the present invention;

fig. 5 is a schematic diagram of a third embodiment of the back clearance self-adaptive adjusting planetary transmission mechanism of the present invention.

In the figure: 1. a drive mechanism; 11. a rotating shaft; 21. a first-stage sun gear; 22. a first-stage planet gear; 23. a primary annular gear; 241. a first-stage rotating arm; 242. a first-level planetary disk; 3. an output shaft; 4. a fixed support; 51. a secondary sun gear; 52. a second-stage planet gear; 53. a secondary annular gear; 541. a second-stage rotating arm; 542. a secondary planet disk; 61. a double planetary gear; 62. a first movable engagement portion; 63. a first movable connecting portion; 64. fixing the rotating arm; 65. fixing the planetary plate; 71. a fixed engagement portion; 72. a fixed connection part; 73. a movable planet carrier; 74. a second movable engagement portion; 75. a second movable connecting portion; 81. a first elastic member; 82. a second elastic member; 83. a third elastic member; 84. and a fourth elastic member.

Detailed Description

In order to facilitate understanding of the present invention, the present invention will be described more fully hereinafter with reference to the accompanying drawings. Preferred embodiments of the present invention are shown in the drawings. The invention may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete.

It will be understood that when an element is referred to as being "secured to" another element, it can be directly on the other element or intervening elements may also be present. When an element is referred to as being "connected" to another element, it can be directly connected to the other element or intervening elements may also be present. The terms "vertical," "horizontal," "left," "right," and the like as used herein are for illustrative purposes only.

Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs. The terminology used in the description of the invention herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. As used herein, the term "and/or" includes any and all combinations of one or more of the associated listed items.

Example one

As shown in fig. 1, a schematic diagram of a back clearance adaptive adjustment planetary transmission mechanism provided in an embodiment of the present invention is shown, which includes a driving mechanism 1, a primary transmission system, an output shaft 3, and a fixed support 4. Wherein the rotational axis 11 of the drive mechanism 1 is axially adjustable. It should be noted that axially adjustable means: the rotary shaft 11 is displaceable in its own axial direction and can be axially restrained when displaced to a predetermined position. Specifically, the driving mechanism 1 may be a motor, and the motor capable of axially adjusting the rotating shaft 11 is a conventional motor, and will not be described herein.

The primary transmission system comprises a primary sun gear 21, a primary planet gear 22, a primary ring gear 23 and a primary planet carrier; the diameters of the root circle and the addendum circle of the primary sun gear 21, the primary planet gear 22 and the primary annular gear 23 are unchanged, and the tooth thicknesses of the primary sun gear 21, the primary planet gear 22 and the primary annular gear 23 are suitable for linear change along the respective axial directions; namely, the primary sun gear 21 and the primary planet gear 22, and the primary ring gear 23 are gears with variable tooth thickness. The primary sun gear 21 is coaxially disposed and fixedly connected to the rotating shaft 11 of the driving mechanism 1, and specifically, the primary sun gear 21 and the rotating shaft 11 of the driving mechanism 1 may be fixedly connected by a common fixed connection manner such as a key connection. The primary annular gear 23 is fixedly arranged, and the primary planet gears 22 are respectively meshed with the outer teeth of the primary sun gear 21 and the inner teeth of the primary annular gear 23; the primary planet carrier includes a primary rotor arm 241 and a primary planet disk 242. The first-stage rotating arms 241 are rotatably connected to the shaft holes of the first-stage planetary gears 22, and specifically, ball bearings are arranged between the first-stage rotating arms 241 and the shaft holes of the first-stage planetary gears 22; the inner ring of the ball bearing is in interference fit with the first-stage rotating arm 241; the outer ring of the ball bearing is in interference fit with the shaft hole of the primary planet gear 22. The first-stage rotating arm 241 is elastically connected with the first-stage planetary plate 242 through a first elastic piece 81; the first elastic member 81 is adapted to apply a force to the primary rotor arm 241 in the axial direction of the primary planet gears 22 so that the external teeth of the primary planet gears 22 have a tendency to approach the internal teeth of the primary ring gear 23; the primary planetary disc 242 is in driving connection with the output shaft 3, the output shaft 3 is rotatably connected in a fixed support 4, and the fixed support 4 is adapted to provide radial support force to the output shaft 3.

In the above arrangement, the rotating shaft 11 of the driving mechanism 1 can be axially adjusted, so that the axial position of the primary sun gear 21 can be adjusted, and the running clearance between the primary sun gear 21 and the primary planet gears 22 can be eliminated by adjusting the axial position of the primary sun gear 21, thereby ensuring the transmission precision. The first elastic element 81 can provide pretightening force between the primary planet gears 22 and the primary ring gear 23 which are meshed with each other, and when a gap is generated due to abrasion between the primary planet gears 22 and the primary ring gear 23 which are meshed with each other, the axial position of the primary planet gears 22 can be automatically adjusted by the first elastic element 81 under the action of elastic force, so that the primary planet gears 22 and the primary ring gear 23 are meshed more tightly, the back gap of gear transmission is reduced, and the transmission precision is ensured. The working principle of the back clearance self-adaptive adjustment planetary transmission mechanism is as follows: the rotating shaft 11 of the driving mechanism 1 drives the first-stage sun gear 21 to rotate, and the first-stage ring gear 23 is fixedly arranged, so that the first-stage planet gears 22 rotate and revolve around the first-stage sun gear 21, the revolving first-stage planet gears 22 drive the first-stage planet carrier to rotate, and the rotating first-stage planet carrier drives the output shaft 3 to rotate to output power.

Preferably, referring to fig. 2, a two-stage transmission system is provided between the primary planetary disk 242 and the output shaft 3, and the transmission ratio of the planetary transmission mechanism can be further increased by providing the two-stage transmission system. The secondary transmission system comprises a secondary sun gear 51, a secondary planet gear 52, a secondary ring gear 53 and a secondary planet carrier; the diameters of the root circle and the tip circle of the secondary sun gear 51, the secondary planet gear 52 and the secondary ring gear 53 are constant, and the tooth thicknesses of the secondary sun gear 51, the secondary planet gear 52 and the secondary ring gear 53 are suitable for linear change along the respective axial directions, i.e. the secondary sun gear 51, the secondary planet gear 52 and the secondary ring gear 53 are all variable tooth thickness gears. The secondary sun gear 51 is coaxially arranged with the primary planet disc 242 and is in transmission connection with the primary planet disc; the secondary ring gear 53 is fixedly arranged, and the secondary planet gears 52 are respectively meshed with the outer teeth of the secondary sun gear 51 and the inner teeth of the secondary ring gear 53. The secondary planet carrier comprises a secondary rotating arm 541 and a secondary planet disc 542; the second-stage rotating arm 541 is rotatably connected to the shaft hole of the second-stage planetary gear 52, and specifically, a ball bearing is also arranged between the second-stage rotating arm 541 and the shaft hole of the second-stage planetary gear 52; the inner ring of the ball bearing is in interference fit with the second-stage rotating arm 541; the outer ring of the ball bearing is in interference fit with the shaft hole of the secondary planet gear 52. The second-stage rotating arm 541 is elastically connected with the second-stage planetary plate 542 through a second elastic part 82; the second elastic member 82 is adapted to apply a force to the secondary rotor arms 541 in the axial direction of the secondary planetary gears 52 so that the outer teeth of the secondary planetary gears 52 have a tendency to approach the inner teeth of the secondary ring gear 53; the secondary planetary plate 542 is in driving connection with the output shaft 3. The elastic force of the second elastic member 82 is greater than that of the first elastic member 81.

In the above arrangement, the rotating shaft 11 of the driving mechanism 1 is axially adjustable, so that the axial position of the primary sun gear 21 is adjustable, and the running clearance between the primary sun gear 21 and the primary planet gears 22 can be eliminated by adjusting the axial position of the primary sun gear 21, thereby ensuring the transmission precision. The first elastic member 81 can provide a pretightening force between the first-stage planetary gears 22 and the first-stage ring gear 23 which are meshed with each other, and when a gap is generated due to abrasion between the first-stage planetary gears 22 and the first-stage ring gear 23 which are meshed with each other, the first elastic member 81 can automatically adjust the axial position of the first-stage planetary gears 22 under the action of the elastic force, so that the primary planetary gears 22 and the first-stage ring gear 23 are meshed more tightly. The second elastic element 82 can provide a preload between the second-stage planetary gears 52 and the second-stage ring gear 53 which are meshed with each other, and when a gap is generated due to abrasion between the second-stage planetary gears 52 and the second-stage ring gear 53 which are meshed with each other, the second elastic element 82 can automatically adjust the axial position of the second-stage planetary gears 52 under the action of elastic force, so that the meshing between the second-stage planetary gears 52 and the second-stage ring gear 53 is tighter.

In the above arrangement, when the first elastic member 81 applies a force to the first-stage rotating arm 241 along the axial direction of the first-stage planet gears 22, an opposite force is also applied to the second-stage sun gear 51, so that the second-stage sun gear 51 and the second-stage planet gears 52 tend to move away from each other, and the elastic force of the second elastic member 82 is greater than the elastic force of the first elastic member 81, so that the second-stage planet gears 52 and the second-stage sun gear 51 generally still tend to approach each other, so that the second-stage planet gears 52 and the second-stage sun gear 51 can be engaged tightly at all times, and the transmission precision is ensured. The working principle of the back clearance self-adaptive adjustment planetary transmission mechanism is as follows: the rotating shaft 11 of the driving mechanism 1 drives the first-stage sun gear 21 to rotate, the first-stage planet gears 22 rotate and revolve around the first-stage sun gear 21 due to the fixed arrangement of the first-stage ring gear 23, the revolving first-stage planet gears 22 drive the first-stage planet carrier to rotate, the rotation of the first-stage planet carrier drives the second-stage sun gear 51 to rotate, and the second-stage ring gear 53 is also fixed, so the second-stage planet gears 52 rotate and revolve around the second-stage sun gear 51, the revolving second-stage planet gears 52 drive the second-stage planet carrier to rotate, and the rotating second-stage planet carrier drives the output shaft 3 to rotate to output power.

Preferably, as shown in fig. 3, the rotating shaft 11 and the output shaft 3 of the driving mechanism 1 are hollow shafts, and the centers of the primary planetary disk 242 and the secondary planetary disk 542 are provided with through holes. Through such a setting mode, the wiring can be facilitated.

Example two

As shown in fig. 4, the schematic diagram of the back clearance adaptive adjustment planetary transmission mechanism provided by the second embodiment of the present invention is shown, which includes a driving mechanism 1, a first-stage sun gear 21, a duplex planetary gear 61, a first movable ring gear, a fixed planet carrier, a second-stage sun gear 51, a second-stage planet gear 52, a second-stage ring gear 53, a second-stage planet carrier, an output shaft 3, and a fixed support 4. The rotating shaft 11 of the driving mechanism 1 can be axially adjusted, and the primary sun gear 21 and the rotating shaft 11 of the driving mechanism 1 are coaxially arranged and fixedly connected. A first end of the double planetary gear 61 is engaged with the external teeth of the primary sun gear 21, and a second end of the double planetary gear 61 is engaged with the internal teeth of the first movable ring gear. The fixed planet carrier comprises a fixed rotating arm 64 and a fixed planet disk 65; the first movable inner gear ring comprises a first movable engagement part 62 and a first movable connection part 63; the fixed rotation arm 64 is rotatably connected to the shaft holes of the double planetary gears 61.

The fixed rotation arm 64 is elastically connected to the fixed planetary plate 65 by a first elastic member 81 and/or the first movable engaging portion 62 is connected to the first movable connecting portion 63 by a third elastic member 83. The first elastic member 81 is adapted to apply a force to the fixed rotating arm 64 in the axial direction of the double planetary teeth 61 such that the second ends of the double planetary teeth 61 have a tendency to approach the first movable ring gear; the third elastic member 83 is adapted to apply a force to the first movable meshing portion 62 in the axial direction of the double planetary teeth 61 so that the first movable meshing portion 62 has a tendency to approach the second ends of the double planetary teeth 61.

The secondary sun gear 51 is coaxially arranged with the first movable connecting part 63 and is in transmission connection with the first movable connecting part; the secondary inner gear ring 53 is fixedly arranged, and the secondary planet gears 52 are respectively meshed with the outer teeth of the secondary sun gear 51 and the inner teeth of the secondary inner gear ring 53; the secondary planet carrier comprises a secondary rotating arm 541 and a secondary planet disc 542; the second-stage rotating arm 541 is rotatably connected to the shaft hole of the second-stage planetary gear 52, and the second-stage rotating arm 541 is elastically connected with the second-stage planetary disk 542 through a second elastic member 82; the second elastic member 82 is adapted to apply a force to the secondary rotor arms 541 in the axial direction of the secondary planetary gears 52 so that the outer teeth of the secondary planetary gears 52 have a tendency to approach the inner teeth of the secondary ring gear 53; the secondary planetary disc 542 is in transmission connection with the output shaft 3, the output shaft 3 is rotatably connected in a fixed support 4, and the fixed support 4 is suitable for providing radial supporting force for the output shaft 3; the elastic force of the second elastic member 82 is greater than the elastic force of the third elastic member 83 and the elastic force of the first elastic member 81.

It should be noted that, the fixed rotation arm 64 is elastically connected to the fixed planetary plate 65 by the first elastic member 81 and/or the first movable engaging portion 62 is connected to the first movable connecting portion 63 by the third elastic member 83, it should be understood that the first elastic member 81 and the third elastic member 83 can be used either or both.

In the above arrangement, the rotating shaft 11 of the driving mechanism 1 can be axially adjusted, so that the axial position of the first-stage sun gear 21 can be adjusted, and the running clearance between the first-stage sun gear 21 and the duplex planetary gear 61 can be eliminated by adjusting the axial position of the first-stage sun gear 21, thereby ensuring the transmission precision.

When the fixed rotating arm 64 is elastically connected with the fixed planetary plate 65 through the first elastic member 81 and the first movable engaging portion 62 is rigidly connected with the first movable connecting portion 63, the first elastic member 81 can provide a pretightening force between the intermeshing double planetary teeth 61 and the first movable ring gear, and when a gap is generated due to abrasion between the intermeshing double planetary teeth 61 and the first movable ring gear, the first elastic member 81 can automatically adjust the axial position of the double planetary teeth 61 under the action of the elastic force, so that the intermeshing between the double planetary teeth 61 and the first movable ring gear is tighter; when a gap is generated due to abrasion between the two-stage planetary gears 52 and the two-stage ring gear 53 which are meshed with each other, the second elastic element 82 can automatically adjust the axial position of the two-stage planetary gears 52 under the action of elastic force, so that the meshing between the two-stage planetary gears 52 and the two-stage ring gear 53 is tighter, and the transmission precision is ensured.

When the first movable engaging portion 62 is connected with the first movable connecting portion 63 through the third elastic member 83 and the fixed rotating arm 64 is rigidly connected with the fixed planetary plate 65, the third elastic member 83 may provide a pre-tightening force between the intermeshing double planetary teeth 61 and the first movable ring gear, and when a gap is generated due to abrasion between the intermeshing double planetary teeth 61 and the first movable ring gear, the third elastic member 83 may automatically adjust an axial position of the first movable ring gear under the action of the elastic force, so that the intermeshing between the double planetary teeth 61 and the first movable ring gear is tighter; when a gap is generated due to abrasion between the two-stage planetary gears 52 and the two-stage ring gear 53 which are meshed with each other, the second elastic element 82 can automatically adjust the axial position of the two-stage planetary gears 52 under the action of elastic force, so that the meshing between the two-stage planetary gears 52 and the two-stage ring gear 53 is tighter, and the transmission precision is ensured.

When the fixed rotating arm 64 and the fixed planetary plate 65 are elastically connected through the first elastic member 81 and the first movable engaging portion 62 and the first movable connecting portion 63 are connected through the third elastic member 83, the first elastic member 81 and the third elastic member 83 can provide a pre-tightening force between the dual planetary gear 61 and the first movable ring gear, which are engaged with each other. And when the intermeshing double planetary gears 61 and the first movable ring gear are worn to generate a gap, the first elastic member 81 may automatically adjust the axial position of the double planetary gears 61 under the action of elastic force, so that the intermeshing between the double planetary gears 61 and the first movable ring gear is tighter, and the third elastic member 83 may automatically adjust the axial position of the first movable ring gear under the action of elastic force, so that the intermeshing between the double planetary gears 61 and the first movable ring gear is tighter. When the secondary planet gears 52 and the secondary ring gear 53 which are meshed with each other are worn to generate gaps, the second elastic elements 82 can automatically adjust the axial position of the secondary planet gears 52 under the action of elastic force, so that the meshing between the secondary planet gears 52 and the secondary ring gear 53 is tighter.

In the above arrangement, when the first elastic member 81 applies a force to the fixed rotating arm 64 along the axial direction of the first-stage planet gears 22, the first movable ring gear tends to move towards the second elastic member 82, so that the second-stage sun gears 51 and the second-stage planet gears 52 tend to move away from each other, and the elastic force of the second elastic member 82 is greater than the elastic force of the first elastic member 81, so that the second-stage planet gears 52 and the second-stage sun gears 51 generally tend to still approach each other, and the meshing between the first movable ring gear and the dual gears is tighter. When the third elastic member 83 applies a force to the fixed rotating arm 64 along the axial direction of the primary planet gears 22, an opposite force is applied to the secondary sun gear 51, so that the secondary sun gear 51 and the secondary planet gears 52 tend to move away from each other, and the elastic force of the second elastic member 82 is larger than that of the third elastic member 83, so that the secondary planet gears 52 and the secondary sun gear 51 generally still tend to move close to each other, and the secondary planet gears 52 and the secondary sun gear 51 can be tightly meshed, so that the transmission precision is ensured.

EXAMPLE III

As shown in fig. 5, the schematic diagram of the back clearance adaptive adjustment planetary transmission mechanism provided in the third embodiment of the present invention is shown, which includes a driving mechanism 1, a first-stage sun gear 21, a duplex planetary gear 61, a fixed ring gear, a movable planet carrier 73, a second movable ring gear, an output shaft 3, and a fixed support 4. The rotating shaft 11 of the driving mechanism 1 can be axially adjusted, and the primary sun gear 21 and the rotating shaft 11 of the driving mechanism 1 are coaxially arranged and fixedly connected. The first ends of the duplex planet gears 61 are respectively meshed with the primary sun gear 21 and the fixed inner gear ring, and the second ends of the duplex planet gears 61 are meshed with the second movable inner gear ring. The movable planet carrier 73 is rotatably connected with the duplex planet gear 61; the fixed ring gear includes a fixed engagement portion 71 and a fixed connection portion 72; the second movable ring gear includes a second movable engagement portion 74 and a second movable connection portion 75.

The fixed engaging portion 71 and the fixed connecting portion 72 are elastically connected by a fourth elastic member 84 and/or the second movable engaging portion 74 and the second movable connecting portion 75 are connected by a third elastic member 83. The fourth elastic member 84 is adapted to apply a force to the double planetary gears 61 in the axial direction of the double planetary gears 61 so that the second ends of the double planetary gears 61 have a tendency to approach the second movable ring gear; the third elastic member 83 is adapted to apply a force to the second movable meshing portion 74 in the axial direction of the double planetary gears 61 so that the second movable meshing portion 74 has a tendency to approach the second ends of the double planetary gears 61; the second movable connecting portion 75 is in driving connection with the output shaft 3, the output shaft 3 is rotatably connected in the fixed support member 4, and the fixed support member 4 is adapted to provide radial supporting force to the output shaft 3. The planetary transmission mechanism in the embodiment is an NGWN type planetary transmission mechanism.

It should be noted that, the fixed engaging portion 71 and the fixed connecting portion 72 are elastically connected by the fourth elastic member 84 and/or the second movable engaging portion 74 and the second movable connecting portion 75 are connected by the third elastic member 83, and it should be understood that the third elastic member 83 and the fourth elastic member 84 can be used either or both.

When the fixed meshing part 71 is elastically connected with the fixed connecting part 72 through the fourth elastic member 84 and the second movable meshing part 74 is rigidly connected with the second movable connecting part 75, the fourth elastic member 84 can provide pre-tightening force between the meshed fixed meshing part 71 and the duplex planetary teeth 61, and when a gap is generated due to abrasion between the meshed fixed meshing part 71 and the duplex planetary teeth 61, the fourth elastic member 84 can automatically adjust the axial position of the fixed meshing part 71 under the action of the elastic force, so that the meshing between the fixed meshing part 71 and the duplex planetary teeth 61 is tighter; in addition, the fourth elastic member 84 also makes the engagement between the double planetary gears 61 and the second movable engaging portion 74 tighter.

When the second movable meshing part 74 is connected with the second movable connecting part 75 through the third elastic element 83 and the fixed meshing part 71 is rigidly connected with the fixed connecting part 72, the third elastic element 83 can provide pre-tightening force between the second movable meshing part 74 and the duplex planetary teeth 61 which are meshed with each other, and when a gap is generated due to abrasion between the second movable meshing part 74 and the duplex planetary teeth 61 which are meshed with each other, the third elastic element 83 can automatically adjust the axial position of the second movable meshing part 74 under the action of elastic force, so that the meshing between the second movable meshing part 74 and the duplex planetary teeth 61 is tighter; in addition, the third elastic member 83 also makes the meshing between the double planetary gears 61 and the fixed meshing portion 71 tighter.

When the fixed meshing portion 71 is elastically connected to the fixed connecting portion 72 through the fourth elastic member 84 and the second movable meshing portion 74 is connected to the second movable connecting portion 75 through the third elastic member 83, the fourth elastic member 84 can provide a preload between the fixed meshing portion 71 and the duplex planetary teeth 61, which are meshed with each other, and the third elastic member 83 can provide a preload between the second movable meshing portion 74 and the duplex planetary teeth 61, which are meshed with each other. When a gap is generated due to abrasion between the mutually meshed fixed meshing part 71 and the duplex planet gears 61, the fourth elastic element 84 can automatically adjust the axial position of the fixed meshing part 71 under the action of elastic force, so that the meshing between the fixed meshing part 71 and the duplex planet gears 61 is tighter; when the second movable meshing part 74 and the double planetary gears 61 which are meshed with each other are worn to generate gaps, the third elastic member 83 can automatically adjust the axial position of the second movable meshing part 74 under the action of elastic force, so that the second movable meshing part 74 and the double planetary gears 61 are meshed more tightly.

It should be noted that the approaching and departing mentioned in the present invention should be understood as follows: when the gears with the variable tooth thickness move in the axial direction, the gears move closer to each other in the direction in which the gap between the gears becomes smaller, and move farther from each other in the direction in which the gap between the gears becomes larger.

The utility model also discloses a speed reducer, it includes reduction box and back clearance self-adaptation regulation planetary drive as before, and back clearance self-adaptation regulation planetary drive installs in reduction box.

The above is only the embodiment of the present invention, not limiting the scope of the present invention, all the equivalent structures or equivalent processes of the present invention are used in the specification and the attached drawings, or directly or indirectly applied to other related technical fields, and all the same principles are included in the protection scope of the present invention.

Claims

1. A back clearance self-adaptive adjustment planetary transmission mechanism is characterized by comprising: the driving mechanism, the primary transmission system, the output shaft and the fixed support piece; the primary transmission system comprises primary sun gears, primary planet gears, a primary inner gear ring and a primary planet carrier; the rotating shaft of the driving mechanism can be axially adjusted, and the primary sun gear and the rotating shaft of the driving mechanism are coaxially arranged and fixedly connected; the primary inner gear ring is fixedly arranged, and the primary planet gears are respectively meshed with the primary sun gear and the primary inner gear ring; the first-stage planet carrier comprises a first-stage rotating arm and a first-stage planet disc; the first-stage rotating arm is rotatably connected to a shaft hole of the first-stage planetary gear, and the first-stage rotating arm is elastically connected with the first-stage planetary disk through a first elastic piece; the first elastic part is suitable for applying force to the primary rotating arm along the axial direction of the primary planet gear so that the primary planet gear tends to approach the primary inner gear ring; the first-stage planetary disc is in transmission connection with the output shaft, the output shaft is rotatably connected in the fixed supporting piece, and the fixed supporting piece is suitable for providing radial supporting force for the output shaft.

2. The backlash adaptive control planetary gear as claimed in claim 1, wherein the diameters of the root circle and the tip circle of the primary sun gear, the primary planet gear, and the primary ring gear are constant, and the tooth thicknesses of the primary sun gear, the primary planet gear, and the primary ring gear are adapted to be linearly varied in the respective axial directions.

3. The backlash adaptive adjustment planetary gear according to claim 1, wherein a secondary transmission system is provided between the primary planetary disk and the output shaft, and the secondary transmission system includes a secondary sun gear, a secondary planet gear, a secondary ring gear, and a secondary planet carrier; the secondary sun gear is coaxially arranged with the primary planetary disk and is in transmission connection with the primary planetary disk; the secondary inner gear ring is fixedly arranged, and the secondary planet gear is respectively meshed with the secondary sun gear and the secondary inner gear ring; the secondary planet carrier comprises a secondary rotating arm and a secondary planet disc; the second-stage rotating arm is rotatably connected to a shaft hole of the second-stage planetary gear, and the second-stage rotating arm is elastically connected with the second-stage planetary disk through a second elastic piece; the second elastic part is suitable for applying force to the secondary rotating arm along the axial direction of the secondary planet teeth so that the secondary planet teeth have the tendency of approaching to the secondary inner gear ring; and the secondary planetary disk is in transmission connection with the output shaft.

4. The backlash adaptive control planetary gear according to claim 3, wherein an elastic force of the second elastic member is larger than an elastic force of the first elastic member.

5. The backlash adaptive adjustment planetary gear set as claimed in claim 3, wherein the diameters of the root circle and the tip circle of the secondary sun gear, the secondary planet gear, and the secondary ring gear are constant, and the tooth thicknesses of the secondary sun gear, the secondary planet gear, and the secondary ring gear are adapted to vary linearly in the respective axial directions.

6. The backlash adaptive control planetary transmission as in claim 3, wherein the rotating shaft and the output shaft of the driving mechanism are hollow shafts, and the centers of the primary planetary disk and the secondary planetary disk are provided with through holes.

7. The backlash adaptive control planetary gear according to claim 1, wherein a ball bearing is provided between the primary tumbler and the shaft hole of the primary planet gear; the inner ring of the ball bearing is in interference fit with the first-stage rotating arm; and the outer ring of the ball bearing is in interference fit with the shaft hole of the primary planet gear.

8. A back clearance self-adaptive adjustment planetary transmission mechanism is characterized by comprising: the planetary gear type planetary gear set comprises a driving mechanism, a primary sun gear, a duplex planet gear, a first movable inner gear ring, a fixed planet carrier, a secondary sun gear, a secondary planet gear, a secondary inner gear ring, a secondary planet carrier, an output shaft and a fixed support piece; the rotating shaft of the driving mechanism can be axially adjusted, and the primary sun gear and the rotating shaft of the driving mechanism are coaxially arranged and fixedly connected; the first end of the duplex planet gear is meshed with the first-stage sun gear, and the second end of the duplex planet gear is meshed with the inner gear of the first movable inner gear ring; the fixed planet carrier comprises a fixed rotating arm and a fixed planet disk; the first movable inner gear ring comprises a first movable meshing part and a first movable connecting part; the fixed rotating arm is rotatably connected with the shaft hole of the duplex planet gear; the fixed rotating arm is elastically connected with the fixed planetary plate through a first elastic part and/or the first movable meshing part is connected with the first movable connecting part through a third elastic part; the first elastic member is adapted to apply a force to the fixed boom in an axial direction of the duplex planetary gear such that the second end of the duplex planetary gear has a tendency to approach the first movable ring gear; the third elastic member is adapted to apply a force to the first movable meshing portion in an axial direction of the double planetary gear so that the first movable meshing portion has a tendency to approach the second ends of the double planetary gears; the second-stage sun gear is coaxially arranged with the first movable connecting part and is in transmission connection with the first movable connecting part; the secondary inner gear ring is fixedly arranged, and the secondary planet gear is respectively meshed with the secondary sun gear and the secondary inner gear ring; the secondary planet carrier comprises a secondary rotating arm and a secondary planet disc; the second-stage rotating arm is rotatably connected to a shaft hole of the second-stage planetary gear, and the second-stage rotating arm is elastically connected with the second-stage planetary disk through a second elastic piece; the second elastic part is suitable for applying force to the secondary rotating arm along the axial direction of the secondary planet teeth so that the secondary planet teeth have the tendency of approaching to the secondary inner gear ring; the secondary planetary disc is in transmission connection with the output shaft, the output shaft is rotatably connected in the fixed support part, and the fixed support part is suitable for providing radial supporting force for the output shaft; the elasticity of the second elastic member is greater than the elasticity of the third elastic member and the elasticity of the first elastic member.

9. A back clearance self-adaptive adjustment planetary transmission mechanism is characterized by comprising: the driving mechanism, the primary sun gear, the duplex planet gear, the fixed inner gear ring, the movable planet carrier, the second movable inner gear ring, the output shaft and the fixed support piece; the rotating shaft of the driving mechanism can be axially adjusted, and the primary sun gear and the rotating shaft of the driving mechanism are coaxially arranged and fixedly connected; the first ends of the duplex planet gears are respectively meshed with the primary sun gear and the fixed inner gear ring, and the second ends of the duplex planet gears are meshed with the second movable inner gear ring; the movable planet carrier is rotatably connected with the double planetary gears; the fixed annular gear comprises a fixed meshing part and a fixed connecting part; the second movable inner gear ring comprises a second movable meshing part and a second movable connecting part; the fixed engaging part is elastically connected with the fixed connecting part through a fourth elastic part and/or the second movable engaging part is connected with the second movable connecting part through a third elastic part; the fourth elastic element is suitable for applying force to the duplex planet gears along the axial direction of the duplex planet gear teeth so that the second ends of the duplex planet gears have the tendency of approaching the second movable inner gear ring; the third elastic member is adapted to apply a force to the second movable meshing portion in an axial direction of the double planetary gear so that the second movable meshing portion has a tendency to approach the second ends of the double planetary gears; the second movable connecting part is in transmission connection with the output shaft, the output shaft is rotatably connected in the fixed supporting part, and the fixed supporting part is suitable for providing radial supporting force for the output shaft.

10. A reducer comprising a reducer housing and a back-lash-adaptive-adjustment planetary drive mechanism as claimed in any one of claims 1 to 9, mounted within the reducer housing.