CN116592097A - Planetary reducer with different transmission ratios for forward and reverse rotation - Google Patents
Planetary reducer with different transmission ratios for forward and reverse rotation Download PDFInfo
- Publication number
- CN116592097A CN116592097A CN202310871082.6A CN202310871082A CN116592097A CN 116592097 A CN116592097 A CN 116592097A CN 202310871082 A CN202310871082 A CN 202310871082A CN 116592097 A CN116592097 A CN 116592097A
- Authority
- CN
- China
- Prior art keywords
- gear
- shaft sleeve
- sun gear
- input shaft
- different transmission
- 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.)
- Granted
Links
- 230000005540 biological transmission Effects 0.000 title claims abstract description 30
- 239000003638 chemical reducing agent Substances 0.000 title claims abstract description 23
- 238000005096 rolling process Methods 0.000 claims description 4
- 238000004519 manufacturing process Methods 0.000 claims 1
- 238000000034 method Methods 0.000 claims 1
- 239000004065 semiconductor Substances 0.000 claims 1
- 238000010586 diagram Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000002457 bidirectional effect Effects 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
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
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/46—Gearings having only two central gears, connected by orbital gears
-
- 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
- F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
-
- 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
-
- 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
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Retarders (AREA)
Abstract
The invention discloses a planetary reducer capable of rotating forward and backward and having different transmission ratios, and belongs to the technical field of planetary reducers. The planetary gear comprises a shell, a fixed shaft fixedly arranged in the shell, an input shaft sleeve and an output shaft sleeve which are sleeved on the fixed shaft in a rotating mode, a planet carrier fixedly arranged on the output shaft sleeve, a power assembly for driving the input shaft sleeve to rotate, a sun gear A and an annular gear B which are arranged on the input shaft sleeve in a unidirectional rotation mode, the annular gear A, a plurality of planet gears A, a sun gear B and a plurality of planet gears B which are fixedly arranged on the fixed shaft in a unidirectional rotation mode, wherein the fixed shaft is fixedly arranged in the shell. The planetary reducer has reasonable structure, can realize forward and reverse rotation with different transmission ratios by switching transmission paths through rotation reversing in two planetary gear trains with different transmission ratios.
Description
Technical Field
The invention mainly relates to the technical field of planetary reducers, in particular to a planetary reducer with different transmission ratios for forward and reverse rotation.
Background
Compared with the common motor, the planetary reducer is widely applied to low-rotation-speed and high-torque transmission equipment due to the characteristics of small return clearance, compact structure and the like. The planetary reducer in the prior art generally has only one planetary gear train, that is, the planetary reducer in the prior art has the same transmission ratio when rotating forward and backward. Then, in some cases, the rotational speed of the motor in the forward direction is required to be significantly different from that in the reverse direction, such as a quick return mechanism, a forward and reverse mechanism of an automobile, and the like. Therefore, there is a need to design a planetary reducer that switches gear ratios by reversing rotation.
Disclosure of Invention
The technical problems to be solved by the invention are as follows: aiming at the technical problems existing in the prior art, the invention provides the planetary reducer which has a reasonable structure, can realize forward and reverse rotation and has different transmission ratios by switching transmission paths through rotation reversing in planetary gear trains with two different transmission ratios.
In order to solve the problems, the invention provides the following solutions: the planetary reducer with different transmission ratios for forward and reverse rotation comprises a shell, a fixed shaft fixedly arranged in the shell, an input shaft sleeve and an output shaft sleeve which are rotationally sleeved on the fixed shaft, and a planetary frame fixedly arranged on the output shaft sleeve; further comprises: the power assembly is used for driving the input shaft sleeve to rotate, a sun wheel A and an annular gear B which are arranged on the input shaft sleeve are respectively rotated in a unidirectional mode through a unidirectional bearing A and a unidirectional bearing B, the annular gear A which is arranged on the shell is rotated in a unidirectional mode through a unidirectional bearing C, a plurality of planetary gears A which are arranged on the planet carrier in an external meshed mode with the sun wheel A and in an internal meshed mode with the annular gear A and are used for driving, a sun wheel B which is fixedly arranged on the fixed shaft, and a plurality of planetary gears B which are arranged on the planet carrier in an external meshed mode with the sun wheel B and in an internal meshed mode with the annular gear B are used for driving.
When the input shaft sleeve rotates in the forward direction, the one-way bearing A is in a stop state, the one-way bearing B is in a start state, and the one-way bearing C is in a stop state; when the input shaft sleeve reversely rotates, the one-way bearing B is in a stop state, and the one-way bearing A and the one-way bearing C are both in a movement-enabling state; the gear ratio of the inner gear ring A to the sun gear A is not smaller than the gear ratio of the inner gear ring B to the sun gear B.
Further, the power assembly comprises a motor body fixedly arranged on the shell, a driving gear fixedly arranged on an output shaft of the motor body, and a driven gear fixedly arranged on the input shaft sleeve; the driven gear is meshed with the driving gear for transmission.
Further, the planet carrier comprises a disc with a central hole in the center, a plurality of gear shafts A which are arranged in an axisymmetric manner and perpendicular to the end face of the disc, and a plurality of gear shafts B which are arranged in an axisymmetric manner and perpendicular to the end face of the disc; the planetary gear A is rotatably arranged on the gear shaft A, and the planetary gear B is rotatably arranged on the gear shaft B.
Further, one end of the output shaft sleeve is sleeved on the fixed shaft by adopting a rolling bearing, and the other end of the output shaft sleeve penetrates through the shell and extends to the outside of the shell.
Further, the gear ratio of the ring gear a to the sun gear a is equal to the gear ratio of the ring gear B to the sun gear B.
Further, the gear ratio of the inner gear ring A to the sun gear A is larger than the gear ratio of the inner gear ring B to the sun gear B.
Compared with the prior art, the invention has the following advantages and beneficial effects: the planetary reducer with different transmission ratios for forward and reverse rotation is provided with a planetary gear train A consisting of a sun gear A, a planet gear A and an inner gear ring A which are arranged in a unidirectional rotation way, so that when an input shaft sleeve rotates in the forward direction, an output shaft sleeve rotates in the forward direction after being decelerated by the planetary gear train A; the planetary gear system B is composed of a sun gear B which is fixedly arranged, an inner gear ring B which is unidirectionally rotated and a planetary gear B, so that when the input shaft sleeve reversely rotates, the output shaft sleeve reversely rotates and outputs after being decelerated by the planetary gear system B. In addition, when the input shaft sleeve reversely rotates, the one-way bearing C provides a rotational degree of freedom for the annular gear A, so that the gear ratio stability of the input shaft sleeve during reverse rotation is increased. Therefore, the planetary reducer has a reasonable structure, can realize forward and reverse rotation with different transmission ratios by switching transmission paths through rotation reversing in the planetary gear trains with two different transmission ratios.
Drawings
Fig. 1 is a schematic structural diagram of a planetary reducer with different transmission ratios for forward and reverse rotation.
Fig. 2 is a schematic diagram of the structure of the planet carrier in the present invention.
FIG. 3 is a cross-sectional view A-A of FIG. 1.
Fig. 4 is a sectional view of fig. 1B-B.
In the figure, 10-the housing; 11-dead axle; 12-an input sleeve; 13-a planet carrier; 130-a disc; 131-a central hole; 132—gear shaft a; 133-gear shaft B; 14-an output shaft sleeve; 21-sun gear a; 22-planet wheel A; 23-an inner gear ring A; 24-one-way bearing a; 25-a one-way bearing C; 31-sun gear B; 32-planet wheel B; 33-an inner gear ring B; 34-a one-way bearing B; 41-a motor body; 42-a drive gear; 43-driven gear.
Detailed Description
The invention will be described in further detail below with reference to the drawings and the specific examples. For convenience of description, the following is specified: the counterclockwise rotation of the input shaft sleeve 12 is forward rotation, and the clockwise rotation of the input shaft sleeve 12 is reverse rotation; the gear ratio of the inner gear ring A23 and the sun gear A21 isThe gear ratio of the inner gear ring B33 and the sun gear B31 is +.>。
Referring to fig. 1 to 4, the planetary reducer with different transmission ratios for forward and reverse rotation according to the present invention includes a housing 10, a fixed shaft 11 fixedly installed in the housing 10, an input shaft sleeve 12 and an output shaft sleeve 14 rotatably sleeved on the fixed shaft 11, a planet carrier 13 fixedly installed on the output shaft sleeve 14, a power assembly driving the input shaft sleeve 12 to rotate, a sun gear a21 and an annular gear B33 respectively installed on the input shaft sleeve 12 in a unidirectional rotation manner by a unidirectional bearing a24 and a unidirectional bearing B34, an annular gear a23 installed on the housing 10 in a unidirectional rotation manner by a unidirectional bearing C25, a plurality of planetary gears a22 rotatably installed on the planet carrier 13 in external engagement with the sun gear a21 and in internal engagement transmission with the annular gear a23, a sun gear B31 fixedly installed on the fixed shaft 11, and a plurality of planetary gears B32 rotatably installed on the planet carrier 13 in external engagement with the sun gear B31 and in internal engagement transmission with the annular gear B33. In specific implementation, the fixed shaft 11 is arranged in the shell 10 along the horizontal direction, and one end of the fixed shaft 11, which is close to the power assembly, is fixedly connected with the shell 10; the two ends of the input shaft sleeve 12 are respectively connected with the fixed shaft 11 in a bidirectional rotation way by adopting a rolling bearing.
When the input shaft sleeve 12 rotates forwards, the one-way bearing A24 is in a stop state, the one-way bearing B34 is in a start state, and the one-way bearing C25 is in a stop state; when the input shaft sleeve 12 rotates reversely, the one-way bearing B34 is in a stop state, and the one-way bearing A24 and the one-way bearing C25 are in a permitted state; the gear ratio of ring gear a23 to sun gear a21 is not less than the gear ratio of ring gear B33 to sun gear B31, so that the angular velocity of forward rotation of ring gear B33 is less than the angular velocity of forward rotation of input sleeve 12. In specific implementation, the sun gear A21, the planet gear A22 and the annular gear A23 form a planetary gear train A, and the sun gear B31, the planet gear B32 and the annular gear B33 form a planetary gear train B. When the power assembly drives the input shaft sleeve 12 to rotate forward, the sun gear A21 and the input shaft sleeve 12 rotate synchronously in the forward direction, the annular gear B33 lags behind the forward rotation of the input shaft sleeve 12, the annular gear A23 and the shell 10 keep relatively static, and at the moment, the planetary gear train A is a driving gear train, and the planetary gear train B is a driven gear train; when the power assembly drives the input shaft sleeve 12 to reversely rotate, the annular gear B33 and the input shaft sleeve 12 synchronously reversely rotate, the sun gear A21 lags behind the reverse rotation of the input shaft sleeve 12, and the planetary gear train B is a driving gear train and the planetary gear train A is a driven gear train.
Preferably, the power assembly includes a motor body 41 fixedly mounted on the housing 10, a driving gear 42 fixedly mounted on an output shaft of the motor body 41, and a driven gear 43 fixedly mounted on the input shaft sleeve 12; the driven gear 43 is engaged with the driving gear 42. The output shaft of the motor body 41 rotates clockwise, the driving gear 42 rotates clockwise, the driven gear 43 meshed with the driving gear 42 rotates anticlockwise, and the input shaft sleeve 12 rotates forwards; the output shaft of the motor body 41 rotates counterclockwise, the driving gear 42 rotates counterclockwise, the driven gear 43 externally engaged with the driving gear 42 rotates clockwise, and the input shaft housing 12 rotates reversely.
Preferably, the planet carrier 13 comprises a disc 130 with a central hole 131 at the center, a plurality of gear shafts A132 which are arranged in an axisymmetric manner and perpendicular to the end face of the disc 130, and a plurality of gear shafts B133 which are arranged in an axisymmetric manner and perpendicular to the end face of the disc 130; the planet wheel A22 is rotatably arranged on the gear shaft A132, and the planet wheel B32 is rotatably arranged on the gear shaft B133. In practice, the output shaft sleeve 14 passes through the central hole 131 of the planet carrier 13 and is fixedly connected with the planet carrier 13; the number of planet gears a22 is equal to the number of gear shafts a132, and the number of planet gears B32 is equal to the number of gear shafts B133.
Preferably, one end of the output shaft sleeve 14 is fitted on the fixed shaft 11 using a rolling bearing, and the other end thereof penetrates the housing 10 and extends to the outside of the housing 10 and is connected to a load.
As one of the preferable, the gear ratio of the ring gear a23 to the sun gear a21 is equal to the gear ratio of the ring gear B33 to the sun gear B31, and as two of the preferable, the gear ratio of the ring gear a23 to the sun gear a21 is larger than the gear ratio of the ring gear B33 to the sun gear B31. Selecting the gear ratio in the above manner ensures that the rotational speed of ring gear B33 is less than the rotational speed of input sleeve 12 when input sleeve 12 is rotating in the forward direction, so that output sleeve 14 has a stable gear ratio when input sleeve 12 is rotating in the forward direction.
The forward rotation speed reduction working principle of the invention is as follows: when the power assembly drives the input shaft sleeve 12 to rotate positively, the planetary gear train A is an active gear train, namely, in the planetary gear train A, the annular gear A23 is fixed, the sun gear A21 is active input, and the planet carrier 13 and the output shaft sleeve 14 are passive output, so that the angular velocity of the input shaft sleeve 12Angular velocity with the output shaft sleeve 14>The ratio is thatI.e., the rotational angular velocity of the output shaft sleeve 14 is smaller than the rotational angular velocity of the input shaft sleeve 12, thereby realizing the deceleration output of the forward rotation; in this case, the planetary gear system B is a driven wheel system, i.e. in the planetary gear system B, the sun gear B31 is fixed, the planet carrier 13 is active input, and the ring gear B33 is passive output, so that the angular velocity of the output shaft sleeve 14 is +.>Angular velocity with ring gear B33>The ratio is->Therefore, the angular velocity of the input sleeve 12>Angular velocity with ring gear B33>The ratio is thatSince the gear ratio of the ring gear A23 to the sun gear A21 is not smaller than the gear ratio of the ring gear B33 to the sun gear B31, i.e. +.>Therefore, the angular velocity of ring gear B33 +.>Less than the angular velocity of the input sleeve 12 +.>The ring gear B33 is allowed to rotate in the forward direction with hysteresis of the input sleeve 12 under the operation of the one-way bearing B34.
The reverse rotation speed reduction working principle of the invention is as follows: when the power assembly drives the input shaft sleeve 12 to rotate reverselyThe planetary gear train B is an active gear train, i.e. in the planetary gear train B, the sun gear B31 is fixed, the ring gear B33 is active input, the planet carrier 13 and the output sleeve 14 are passive output, and thus the rotational angular velocity of the input sleeve 12With the output shaft sleeve 14->The ratio of the angular velocities of (2) is +.>Thereby realizing the deceleration output of reverse rotation; in the planetary gear train a, the planet carrier 13 is actively input, and the unidirectional bearing C25 in the enabled state provides a rotational degree of freedom for the ring gear a23, that is, the sun gear a21 and the ring gear a23 are both passively output, so that the unidirectional bearing a24 is prevented from being switched from the enabled state to the stop state due to too high rotation speed of the sun gear a21, and stability between the input shaft sleeve 12 and the output shaft sleeve 14 during reverse rotation is increased.
The above is merely a specific embodiment of the present invention, but the scope of the present invention is not limited thereto, and any changes or substitutions that do not undergo the inventive work should fall within the scope of the present invention.
Claims (6)
1. The planetary reducer with different transmission ratios for forward and reverse rotation comprises a shell (10), a fixed shaft (11) fixedly arranged in the shell (10), an input shaft sleeve (12) and an output shaft sleeve (14) rotatably sleeved on the fixed shaft (11), and a planet carrier (13) fixedly arranged on the output shaft sleeve (14); the method is characterized in that: also included is a method of manufacturing a semiconductor device,
the power assembly is used for driving the input shaft sleeve (12) to rotate, a sun gear A (21) and an annular gear B (33) which are arranged on the input shaft sleeve (12) are respectively and unidirectionally rotated by a unidirectional bearing A (24) and a unidirectional bearing B (34), the annular gear A (23) which is arranged on the shell (10) is unidirectionally rotated by a unidirectional bearing C (25), a plurality of planet gears A (22) which are arranged on the planet carrier (13) and are externally meshed with the sun gear A (21) and internally meshed with the annular gear A (23) for transmission are arranged, a sun gear B (31) which is fixedly arranged on the fixed shaft (11), and a plurality of planet gears B (32) which are rotatably arranged on the planet carrier (13) and are externally meshed with the sun gear B (31) and internally meshed with the annular gear B (33);
when the input shaft sleeve (12) rotates positively, the one-way bearing A (24) is in a stop state, the one-way bearing B (34) is in a permitted state, and the one-way bearing C (25) is in a stop state; when the input shaft sleeve (12) rotates reversely, the one-way bearing B (34) is in a stop state, and the one-way bearing A (24) and the one-way bearing C (25) are both in a movable state; the gear ratio of the annular gear A (23) to the sun gear A (21) is not smaller than the gear ratio of the annular gear B (33) to the sun gear B (31).
2. The planetary reducer with different transmission ratios for forward and reverse rotation according to claim 1, wherein: the power assembly comprises a motor body (41) fixedly arranged on the shell (10), a driving gear (42) fixedly arranged on an output shaft of the motor body (41), and a driven gear (43) fixedly arranged on the input shaft sleeve (12); the driven gear (43) is meshed with the driving gear (42) for transmission.
3. The planetary reducer with different transmission ratios for forward and reverse rotation according to claim 1, wherein: the planet carrier (13) comprises a disc (130) with a central hole (131) in the center, a plurality of gear shafts A (132) which are arranged in an axisymmetric manner and perpendicular to the end face of the disc (130), and a plurality of gear shafts B (133) which are arranged in an axisymmetric manner and perpendicular to the end face of the disc (130); the planet wheel A (22) is rotatably arranged on the gear shaft A (132), and the planet wheel B (32) is rotatably arranged on the gear shaft B (133).
4. The planetary reducer with different transmission ratios for forward and reverse rotation according to claim 1, wherein: one end of the output shaft sleeve (14) is sleeved on the fixed shaft (11) by adopting a rolling bearing, and the other end of the output shaft sleeve penetrates through the shell (10) and extends to the outside of the shell (10).
5. The planetary reducer with different transmission ratios for forward and reverse rotation according to claim 1, wherein: the gear ratio of the annular gear A (23) to the sun gear A (21) is equal to the gear ratio of the annular gear B (33) to the sun gear B (31).
6. The planetary reducer with different transmission ratios for forward and reverse rotation according to claim 1, wherein: the gear ratio of the annular gear A (23) to the sun gear A (21) is larger than the gear ratio of the annular gear B (33) to the sun gear B (31).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202310871082.6A CN116592097B (en) | 2023-07-17 | 2023-07-17 | Planetary reducer with different transmission ratios for forward and reverse rotation |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202310871082.6A CN116592097B (en) | 2023-07-17 | 2023-07-17 | Planetary reducer with different transmission ratios for forward and reverse rotation |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN116592097A true CN116592097A (en) | 2023-08-15 |
| CN116592097B CN116592097B (en) | 2023-12-05 |
Family
ID=87608408
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202310871082.6A Active CN116592097B (en) | 2023-07-17 | 2023-07-17 | Planetary reducer with different transmission ratios for forward and reverse rotation |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN116592097B (en) |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20090115422A (en) * | 2008-05-02 | 2009-11-05 | (주)엠비아이 | One way transmission for motor |
| CN102494083A (en) * | 2011-12-23 | 2012-06-13 | 叶羽经 | Constant-speed reverse transfer planetary reducer |
| CN208634289U (en) * | 2018-05-28 | 2019-03-22 | 河北工业大学 | A kind of double outputting planetary gear reduction unit |
| CN209146283U (en) * | 2018-11-09 | 2019-07-23 | 东莞市卓蓝自动化设备有限公司 | A kind of improved planetary reducer |
| CN212616141U (en) * | 2020-06-15 | 2021-02-26 | 重庆彤领机械配件进出口有限公司 | Power integration positive and negative rotation two-gear planetary AT transmission |
| CN212744901U (en) * | 2020-06-15 | 2021-03-19 | 重庆彤领机械配件进出口有限公司 | Power integration forward and reverse rotation three-gear planet rear-mounted throwing block AT transmission |
| CN114992288A (en) * | 2022-07-28 | 2022-09-02 | 常州南鹏机械有限公司 | Flexible transmission planetary reducer |
-
2023
- 2023-07-17 CN CN202310871082.6A patent/CN116592097B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20090115422A (en) * | 2008-05-02 | 2009-11-05 | (주)엠비아이 | One way transmission for motor |
| CN102494083A (en) * | 2011-12-23 | 2012-06-13 | 叶羽经 | Constant-speed reverse transfer planetary reducer |
| CN208634289U (en) * | 2018-05-28 | 2019-03-22 | 河北工业大学 | A kind of double outputting planetary gear reduction unit |
| CN209146283U (en) * | 2018-11-09 | 2019-07-23 | 东莞市卓蓝自动化设备有限公司 | A kind of improved planetary reducer |
| CN212616141U (en) * | 2020-06-15 | 2021-02-26 | 重庆彤领机械配件进出口有限公司 | Power integration positive and negative rotation two-gear planetary AT transmission |
| CN212744901U (en) * | 2020-06-15 | 2021-03-19 | 重庆彤领机械配件进出口有限公司 | Power integration forward and reverse rotation three-gear planet rear-mounted throwing block AT transmission |
| CN114992288A (en) * | 2022-07-28 | 2022-09-02 | 常州南鹏机械有限公司 | Flexible transmission planetary reducer |
Also Published As
| Publication number | Publication date |
|---|---|
| CN116592097B (en) | 2023-12-05 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN202040291U (en) | Clutch-control two-way input and single-way output wheel train capable of reversible transmission | |
| US20080194375A1 (en) | Planetary gear mechanism | |
| JPH01169169A (en) | Toroidal type continuously variable transmission | |
| KR100886384B1 (en) | Two speed planetary gear speed reducer | |
| CN116592097B (en) | Planetary reducer with different transmission ratios for forward and reverse rotation | |
| CN216842951U (en) | Multi-degree-of-freedom transmission mechanism | |
| CN108150637B (en) | Multi-gear EV power device | |
| CN110966360A (en) | Transmission device, control method thereof and automobile | |
| JPH01312249A (en) | Multifunctional gear mechanism | |
| CN102192300A (en) | Lockable or releasable wheel system with bidirectional input and one-way output | |
| CN105480076A (en) | Planetary differential power coupling device | |
| CN106641109A (en) | Small planetary gear reducer with large transmission ratio | |
| KR20210024134A (en) | Vehicle powertrain and vehicle | |
| CN113915300B (en) | Method for realizing stepless speed change transmission with output self-adaptive load characteristic | |
| CN111252234A (en) | Oblique double-acting wing | |
| CN112728022A (en) | Double-speed transmission for electric automobile | |
| CN110878816B (en) | Single/double-input double-output planetary gear reducer | |
| CN113483060A (en) | Torque-dividing gear transmission speed reducer for main speed reducer of coaxial helicopter | |
| CN106828065B (en) | Dual-motor coupling two-stage nutation speed change device and working method thereof | |
| CN215521845U (en) | Planetary reversing mechanism for vibrating steel wheel | |
| CN213655619U (en) | Two-gear transmission | |
| TWI460364B (en) | Speed changing apparatus for motors | |
| CN111750044A (en) | Reversing gear box | |
| CN219570756U (en) | Planetary gear reducer structure with large transmission ratio | |
| CN212131213U (en) | Magnetic reversing transmission device |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |