CN114992288B - Flexible transmission planetary reducer - Google Patents
Flexible transmission planetary reducer Download PDFInfo
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- CN114992288B CN114992288B CN202210899074.8A CN202210899074A CN114992288B CN 114992288 B CN114992288 B CN 114992288B CN 202210899074 A CN202210899074 A CN 202210899074A CN 114992288 B CN114992288 B CN 114992288B
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- 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
- F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
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- 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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
- F16F15/133—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs
- F16F15/134—Wound springs
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- 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
- F16H49/00—Other gearings
- F16H49/001—Wave gearings, e.g. harmonic drive transmissions
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- 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
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/06—Use of materials; Use of treatments of toothed members or worms to affect their intrinsic material properties
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- 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
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/08—Profiling
- F16H55/0833—Flexible toothed member, e.g. harmonic drive
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- 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
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- 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
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
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- 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
- F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
- F16H2001/327—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear with orbital gear sets comprising an internally toothed ring gear
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- 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
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/17—Toothed wheels
- F16H2055/176—Ring gears with inner teeth
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Electromagnetism (AREA)
- Thermal Sciences (AREA)
- Retarders (AREA)
Abstract
The invention discloses a flexible transmission planetary reducer, and belongs to the technical field of planetary reducers. The planetary gear transmission device comprises a shell, an input main shaft and an output main shaft, wherein the input main shaft is coaxially and rotatably arranged on the shell and used for connecting a driving motor shaft, the output main shaft is used for connecting a load, one end of the transmission shaft sleeve is sleeved on the input main shaft in a non-contact mode, the other end of the transmission shaft sleeve is rotatably arranged on the output main shaft, a transmission spring is arranged in the transmission shaft sleeve and sleeved on the input main shaft, a sun gear is fixedly arranged on the transmission shaft sleeve, a planetary carrier is fixedly arranged on the output main shaft, a planetary gear A and a planetary gear B which are rotatably arranged on the planetary carrier and externally meshed with the sun gear, and a flexible double-faced gear ring capable of generating obvious elastic deformation. The planetary reducer is a flexible transmission planetary reducer which is reasonable in structure, has a flexible start-stop sun gear and a flexible transmission planetary gear, improves the rotation stability by absorbing vibration energy of a main shaft, and can be directly connected with a driving motor.
Description
Technical Field
The invention mainly relates to the technical field of planetary speed reducers, in particular to a planetary speed reducer with flexible transmission.
Background
The planetary reducer has the characteristics of small return clearance, compact structure and the like, so that the planetary reducer is widely applied to transmission equipment with low rotating speed and large torque. In a planetary reducer in the prior art, an input main shaft is generally rigidly connected with a sun gear, and a planetary gear is driven by the sun gear to roll on a gear ring, so that a speed reduction effect is achieved. The input main shaft and the output main shaft can be excited by the outside world to generate certain vibration in the rotating process, so that the transmission of the speed reducer is not stable, the rigid connecting structure is easy to generate fatigue damage of the main shaft, and the service life of the speed reducer is shortened; therefore, although the prior art realizes the deceleration effect of the output spindle and the input spindle, certain disadvantages still exist: 1. the input main shaft lacks flexibility in the starting and stopping process; 2. the planet and sun gears lack flexibility during rotation. Therefore, the planetary reducer with flexible transmission has certain practical value.
Disclosure of Invention
The technical problems to be solved by the invention are as follows: aiming at the technical problems in the prior art, the invention provides the flexible transmission planetary reducer which is reasonable in structure, has a flexible start-stop sun gear and a flexible transmission planetary gear, improves the rotation stability by absorbing the vibration energy of a main shaft, and can be directly connected with a driving motor.
In order to solve the problems, the solution proposed by the invention is as follows: a planetary reducer with flexible transmission comprises a shell, an input main shaft and an output main shaft, wherein the input main shaft and the output main shaft are coaxially and rotatably arranged on the shell.
Still include one end non-contact suit and install input spindle is last and the other end rotates and installs the epaxial driving sleeve of output installs the inside and suit of driving sleeve is in epaxial transmission spring of input, the fixed sun gear of installing on the driving sleeve, the fixed planet carrier of installing the epaxial planet carrier of output rotates and installs on the planet carrier with sun gear external toothing's planet wheel A and planet wheel B to and can take place to show elastic deformation's flexible two-sided ring gear.
Two ends of the transmission spring are respectively connected with the input main shaft and the transmission shaft sleeve; the planet wheel A and the planet wheel B are symmetrical relative to the axis of the output main shaft and are in inner meshing transmission with the flexible double-faced gear ring.
Further, the internal surface of shell is equipped with the round shell internal tooth, the outer lane surface of flexible two-sided ring gear be equipped with the ring gear external tooth that the shell internal tooth meshed mutually, its inner circle surface be equipped with planet wheel A and planet wheel B meshed mutually's ring gear internal tooth.
Furthermore, the planet carrier is also rotatably provided with a tensioning gear A and a tensioning gear B which are engaged with the flexible double-faced gear ring and are not contacted with the sun gear, and the central connecting line of the tensioning gear A and the tensioning gear B is crossed with the central connecting line of the planet gear A and the planet gear B.
Furthermore, the initial structure shape of the flexible double-sided gear ring is circular, and the flexible double-sided gear ring is deformed into an ellipse after being meshed with the planet wheel A, the planet wheel B, the tensioning gear A and the tensioning gear B simultaneously; the planet gear A and the planet gear B are positioned on the long elliptic shaft of the flexible double-sided gear ring, and the tensioning gear A and the tensioning gear B are positioned on the short elliptic shaft of the flexible double-sided gear ring; the elliptical flexible double-sided gear ring is in inner meshing transmission with the shell at the end point of the long shaft.
Furthermore, the flexible double-sided gear ring is made of high polymer elastic materials.
Further, the transmission spring is a metal spiral spring, and the spiral direction of the metal spiral spring is the same as the positive rotation direction of the input spindle.
Compared with the prior art, the invention has the following advantages and beneficial effects: the planetary reducer with flexible transmission is provided with the transmission spring and the transmission shaft sleeve which are connected with the input main shaft and the output main shaft, so that the transmission shaft sleeve and the input main shaft rotate relatively to each other in the starting and stopping processes of the input main shaft, and the flexible transmission in the starting and stopping processes of the input main shaft is realized; when the deformation of the transmission spring is not changed any more, the input main shaft and the transmission shaft sleeve are in rigid connection, so that rigid transmission in the normal working process of the input main shaft is realized; in addition, the invention is also provided with a flexible double-sided gear ring which can generate obvious elastic deformation, the flexible double-sided gear ring which is deformed into an ellipse can not rotate relative to the shell, and the positions of the long axis and the short axis of the flexible double-sided gear ring can only be continuously changed along with the rotation of the planet carrier in the rotation process of the planet carrier A and the planet carrier B, so that adaptive elastic deformation is generated, and the flexibility in the movement process of the planet carrier is increased. Therefore, the planetary reducer is a flexible transmission planetary reducer which is reasonable in structure, has a flexible start-stop sun gear and a flexible transmission planetary gear, improves the rotation stability by absorbing the vibration energy of the main shaft, and can be directly connected with a driving motor.
Drawings
Fig. 1 is a schematic structural principle diagram of a flexible transmission planetary reducer of the invention.
Fig. 2 isbase:Sub>A schematic sectional view taken along linebase:Sub>A-base:Sub>A in fig. 1.
Fig. 3 is a schematic structural diagram of a planet carrier after two planet wheels and two tension gears are installed.
In the figure, 1 — housing; 2-input main shaft; 21-input rolling bearing; 3-output spindle; 31-output rolling bearing; 32-rolling bearing a; 33-rolling bearing B; 41-driving shaft sleeve; 42-a transmission spring; 43-sun gear; 44-a planet carrier; 45-planet wheel a; 46-planet wheel B; 47-flexible double-sided gear ring; 51-tensioning gear a; 52-tensioning gear B.
Detailed Description
The invention will be described in further detail below with reference to the accompanying drawings and specific embodiments. For convenience of description, the spiral direction of the transmission spring 42 is not said to be the forward direction.
Referring to fig. 1, the planetary reducer of the present invention comprises a housing 1, an input main shaft 2 coaxially and rotatably mounted on the housing 1 for connecting a driving motor shaft and an output main shaft 3 for connecting a load, a driving shaft sleeve 41 with one end thereof fitted over the input main shaft 2 in a non-contact manner and the other end thereof rotatably mounted on the output main shaft 3, a driving spring 42 mounted inside the driving shaft sleeve 41 and fitted over the input main shaft 2, a sun gear 43 fixedly mounted on the driving shaft sleeve 41, a planetary carrier 44 fixedly mounted on the output main shaft 3, a planetary gear a45 and a planetary gear B46 rotatably mounted on the planetary carrier 44 and externally engaged with the sun gear 43, and a flexible double-sided ring gear 47 capable of undergoing significant elastic deformation. The input main shaft 2 is rotatably arranged on the shell 1 through an input rolling bearing 21, one end of the input main shaft connected with the driving motor extends to the outside of the shell 1, and the other end of the input main shaft extends into the transmission shaft sleeve 41; the output main shaft 3 is a hollow shaft and is rotatably arranged on the shell 1 through an output rolling bearing 31; one end of the driving shaft sleeve 41 is rotatably arranged in the cavity of the output main shaft 3 through a rolling bearing B33 and a rolling bearing A32; the axis of the input main shaft 2 is collinear with the axes of the transmission shaft sleeve 41 and the output main shaft 3; the input main shaft 2 drives the transmission shaft sleeve 41 to rotate through the transmission spring 42, and further drives the sun gear 43 fixedly arranged on the transmission shaft sleeve 41 to rotate; the flexible double-sided ring gear 47 does not rotate relative to the housing 1, and only undergoes a certain elastic deformation, so that the sun gear 43 rotates to drive the planet gears a45 and B46 to rotate, and the planet carrier 44 is driven to rotate, and finally the output main shaft 3 fixedly connected with the planet carrier 44 rotates.
Two ends of the transmission spring 42 are respectively fixedly connected with the input main shaft 2 and the transmission shaft sleeve 41; the planet wheels A45 and B46 are symmetrical about the axis of the output main shaft 3 and are in inner meshing transmission with the flexible double-faced gear ring 47.
Preferably, the planet carrier 44 is also rotatably provided with a tension gear a51 and a tension gear B52 which are engaged with the flexible double-faced gear ring 47 and are not contacted with the sun gear 43, and a central line of the tension gear a51 and the tension gear B52 is crossed with a central line of the planet gear a45 and the planet gear B46. The planet wheels a45 and B46 have the same radius, and the tensioning gear a51 and the tensioning gear B52 have the same radius. During specific implementation, the radius of the planet wheel A45 is larger than that of the tensioning gear A51, so that the rotating speeds of the tensioning gear A51 and the tensioning gear B52 are favorably improved, and the long axis deformation energy and the short axis deformation energy of the flexible double-faced gear ring 47 are well balanced. When the sun wheel 43 rotates, the planet wheels A45 and B46 are driven to rotate through external meshing, and the planet carrier 44 is driven to rotate, and the planet carrier 44 rotates to drive the tension gear A51 and the tension gear B52 to roll along the flexible double-faced gear ring 47. In the process of rotation of the sun gear 43, the positions of the elliptical major axis and the elliptical minor axis of the flexible double-sided gear ring 47 are changed continuously, and the tensioning gear a51 and the tensioning gear B52 are arranged, so that elastic deformation of the flexible double-sided gear ring 47 is more continuous, and unstable deformation caused by overhigh rotation speed of the sun gear 43 is avoided.
Preferably, the transmission spring 42 is a metal coil spring, and the coil direction thereof is the same as the forward rotation direction of the input spindle 2. When the input spindle 2 rotates in the positive direction, firstly, the radius of the inner ring of the transmission spring 42 is reduced, that is, the transmission spring 42 is gradually wound on the input spindle 2, and at this time, the transmission shaft sleeve 41 also rotates but obviously lags behind the input spindle 2; then, the transmission spring 42 is no longer radially deformed, and the transmission sleeve 41 and the input spindle 2 keep rotating synchronously. When the input spindle 2 is changed from the forward rotation to the stop, the output spindle 3 rotates by inertia to drive the driving sleeve 41 to continue rotating, and the radius of the inner ring of the driving spring 42 is gradually increased within a short period of time until the driving sleeve 41 stops rotating. When the input spindle 2 rotates in the opposite direction, firstly, the radius of the inner ring of the transmission spring 42 is increased, that is, the transmission spring 42 expands outwards and gradually clings to the inner wall of the transmission shaft sleeve 41, and at this time, the transmission shaft sleeve 41 also rotates in the opposite direction but lags behind the input spindle 2 obviously; then, the radial deformation of the transmission spring 42 is not increased any more, and the transmission sleeve 41 and the input spindle 2 keep synchronous and reverse rotation.
Preferably, the inner surface of the housing 1 is provided with a ring of housing internal teeth, the outer ring surface of the flexible double-sided ring gear 47 is provided with ring gear external teeth meshing with the housing internal teeth, and the inner ring surface thereof is provided with ring gear internal teeth meshing with the planet gears a45, B46, a tension gear a51 and a tension gear B52.
Referring to fig. 1 and 2, as a preferable mode, the flexible double-sided ring gear 47 is in a circular initial structural shape, and deforms into an ellipse after being meshed with the planet gears a45, the planet gears B46, the tension gear a51 and the tension gear B52 simultaneously, wherein the planet gears a45 and the planet gears B46 are located on the long axis of the ellipse of the flexible double-sided ring gear 47, and the tension gear a51 and the tension gear B52 are located on the short axis of the ellipse of the flexible double-sided ring gear 47; the flexible double-sided ring gear 47 deformed into an elliptical shape is in meshing transmission with housing internal teeth provided on the housing 1 at the end point of the major axis through ring gear external teeth. After the planet wheels A45 and B46 are arranged, the shape of the flexible double-sided gear ring 47 is changed from circular to elliptical, so that certain elastic potential energy is stored, and internal meshing transmission is facilitated. When the sun gear 43 rotates to drive the planet gears a45 and B46 to roll along the inner ring of the flexible double-sided ring gear 47, the flexible double-sided ring gear 47 does not rotate relative to the housing 1 as if the flexible double-sided ring gear 47 were instantaneously fixed where it contacts the housing 1 due to the meshing of the outer teeth of the ring gear at the end point of the long shaft of the flexible double-sided ring gear 47 and the inner teeth of the housing. Therefore, during the rotation of the sun gear 43, the flexible double-sided ring gear 47 will not rotate, but will elastically deform, so that the central connecting line of the planet gear a45 and the planet gear B46 always coincides with the long axis of the flexible double-sided ring gear 47, and the central connecting line of the tension gear a51 and the tension gear B52 always coincides with the short axis of the flexible double-sided ring gear 47.
Preferably, the flexible double-sided ring gear 47 is made of a high polymer elastic material, so that on one hand, the rigidity of the flexible double-sided ring gear 47 can be reduced, and on the other hand, vibration energy from the input spindle 2 and the output spindle 3 can be absorbed through self deformation, thereby improving the stability of the rotation of the sun gear 43.
The working principle of the invention is as follows: the external driving motor drives the input main shaft 2 to rotate in the positive direction, the radius of the inner ring of the transmission spring 42 is gradually reduced, and the transmission shaft sleeve 41 and the sun gear 43 lag behind the positive rotation of the input main shaft 2; when the inner radius of the drive spring 42 is no longer reduced, the outdrive 41 and the sun gear 43 will remain rotating synchronously in the forward direction with the input spindle 2. The external driving motor drives the input main shaft 2 to rotate reversely, the radius of the inner ring of the transmission spring 42 is gradually increased, and the transmission shaft sleeve 41 and the sun gear 43 lag behind the reverse rotation of the input main shaft 2; when the inner radius of the drive spring 42 is no longer increased, the outdrive 41 and the sun gear 43 will remain synchronized for counter-rotation with the input spindle 2. When the input spindle 2 is changed from the forward rotation to the stop state, the driving sleeve 41 continues to keep the forward rotation under the effect of the inertial rotation of the output spindle 3, the radius of the driving spring 42 gradually increases until the initial state is recovered, and then the driving sleeve 41 and the input spindle 2 keep relatively static. When the input spindle 2 is changed from the reverse rotation to the stop state, the driving sleeve 41 continues to keep the reverse rotation under the effect of the inertial rotation of the output spindle 3, the radius of the driving spring 42 is gradually reduced until the initial state is recovered, and then the driving sleeve 41 and the input spindle 2 keep relatively static.
The sun wheel 43 rotates to drive the planet wheel a45 and the planet wheel B46 to roll along the oval flexible double-sided gear ring 47, so as to drive the planet carrier 44 and the output main shaft 3 fixedly connected with the planet carrier 44 to rotate, and drive the load to work. In the process of rotation of the sun wheel 43, the position of the connecting line between the centers of the planet wheels a45 and the planet wheels B46 is changed continuously, that is, the positions of the long axis and the short axis of the flexible double-sided ring gear 47 are changed continuously, so that the flexible double-sided ring gear 47 is subjected to significant elastic deformation, vibration energy from the input spindle 2 and the output spindle 3 is absorbed, and the rotation stability of the input spindle 2 and the output spindle 3 is improved.
The above description is only an embodiment of the present invention, but the scope of the present invention is not limited thereto, and any changes or substitutions that are not thought of through the inventive work should be included in the scope of the present invention.
Claims (1)
1. The utility model provides a flexible transmission's planetary reducer, includes shell (1), coaxial rotatable the installing input main shaft (2) and output main shaft (3) on shell (1), its characterized in that: and also comprises
The gear transmission mechanism comprises a transmission shaft sleeve (41), a transmission spring (42), a sun wheel (43), a planet carrier (44), a planet wheel A (45) and a planet wheel B (46) and a flexible double-sided gear ring (47), wherein one end of the transmission shaft sleeve is sleeved on the input main shaft (2) in a non-contact mode, the other end of the transmission shaft sleeve is rotatably arranged on the output main shaft (3), the transmission spring (42) is arranged in the transmission shaft sleeve (41) in a sleeved mode on the input main shaft (2), the sun wheel (43) is fixedly arranged on the transmission shaft sleeve (41), the planet carrier (44) is fixedly arranged on the output main shaft (3), the planet wheel A (45) and the planet wheel B (46) are rotatably arranged on the planet carrier (44) and are externally meshed with the sun wheel (43), and obvious elastic deformation can occur; the flexible double-sided gear ring (47) is made of high polymer elastic material;
two ends of the transmission spring (42) are respectively connected with the input main shaft (2) and the transmission shaft sleeve (41); the planet wheel A (45) and the planet wheel B (46) are symmetrical about the axis of the output spindle (3) and are both in inner meshing transmission with the flexible double-sided gear ring (47);
the planet carrier (44) is also rotatably provided with a tension gear A (51) and a tension gear B (52) which are engaged with the flexible double-faced gear ring (47) and are not contacted with the sun gear (43), and the central connecting line of the tension gear A (51) and the tension gear B (52) is crossed with the central connecting line of the planet gear A (45) and the planet gear B (46);
the inner surface of the shell (1) is provided with a circle of shell inner teeth, the outer ring surface of the flexible double-sided gear ring (47) is provided with gear ring outer teeth meshed with the shell inner teeth, and the inner ring surface of the flexible double-sided gear ring is provided with gear ring inner teeth meshed with the planet gear A (45) and the planet gear B (46);
the initial structure shape of the flexible double-sided gear ring (47) is circular, and the flexible double-sided gear ring is simultaneously meshed with the planet wheel A (45), the planet wheel B (46), the tensioning gear A (51) and the tensioning gear B (52) and then deforms into an oval shape; the planet gears A (45) and B (46) are positioned on the long ellipse axis of the flexible double-sided gear ring (47), and the tension gear A (51) and the tension gear B (52) are positioned on the short ellipse axis of the flexible double-sided gear ring (47); the elliptical flexible double-sided gear ring (47) is in inner gearing transmission with the shell (1) at the end point of the long axis;
the transmission spring (42) is a metal spiral spring, and the spiral direction of the metal spiral spring is the same as the positive rotation direction of the input main shaft (2).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210899074.8A CN114992288B (en) | 2022-07-28 | 2022-07-28 | Flexible transmission planetary reducer |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210899074.8A CN114992288B (en) | 2022-07-28 | 2022-07-28 | Flexible transmission planetary reducer |
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| CN114992288A CN114992288A (en) | 2022-09-02 |
| CN114992288B true CN114992288B (en) | 2022-12-09 |
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| CN202210899074.8A Active CN114992288B (en) | 2022-07-28 | 2022-07-28 | Flexible transmission planetary reducer |
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Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115366673B (en) * | 2022-10-24 | 2023-02-14 | 溧阳市新力机械铸造有限公司 | Gear shaft device for new energy automobile |
| CN116592097B (en) * | 2023-07-17 | 2023-12-05 | 溧阳常大技术转移中心有限公司 | Planetary reducer with different transmission ratios for forward and reverse rotation |
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|---|---|---|---|---|
| WO2013072673A1 (en) * | 2011-11-14 | 2013-05-23 | Gplsquared Limited | Improved harmonic drive |
| CN205841637U (en) * | 2016-06-15 | 2016-12-28 | 广州启帆工业机器人有限公司 | A kind of planet-gear speed reducer |
| CN206159378U (en) * | 2016-11-03 | 2017-05-10 | 青龙满族自治县金轮水电设备有限公司 | Machinery soft start planet gear |
| CN108468760A (en) * | 2018-06-04 | 2018-08-31 | 昆山汉升达传动科技有限公司 | Internal tooth flexbile gear speed reducer |
| CN214331371U (en) * | 2020-12-31 | 2021-10-01 | 山东立人智能科技有限公司 | Planetary gear train and planetary reducer capable of automatically eliminating gaps in radial direction |
-
2022
- 2022-07-28 CN CN202210899074.8A patent/CN114992288B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2013072673A1 (en) * | 2011-11-14 | 2013-05-23 | Gplsquared Limited | Improved harmonic drive |
| CN205841637U (en) * | 2016-06-15 | 2016-12-28 | 广州启帆工业机器人有限公司 | A kind of planet-gear speed reducer |
| CN206159378U (en) * | 2016-11-03 | 2017-05-10 | 青龙满族自治县金轮水电设备有限公司 | Machinery soft start planet gear |
| CN108468760A (en) * | 2018-06-04 | 2018-08-31 | 昆山汉升达传动科技有限公司 | Internal tooth flexbile gear speed reducer |
| CN214331371U (en) * | 2020-12-31 | 2021-10-01 | 山东立人智能科技有限公司 | Planetary gear train and planetary reducer capable of automatically eliminating gaps in radial direction |
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| CN114992288A (en) | 2022-09-02 |
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