CN113803383A - Overload protection anti-slip device - Google Patents
Overload protection anti-slip device Download PDFInfo
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- CN113803383A CN113803383A CN202111157811.9A CN202111157811A CN113803383A CN 113803383 A CN113803383 A CN 113803383A CN 202111157811 A CN202111157811 A CN 202111157811A CN 113803383 A CN113803383 A CN 113803383A
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- Prior art keywords
- gear
- actuator
- clamping ring
- small shaft
- overload protection
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D43/00—Automatic clutches
- F16D43/02—Automatic clutches actuated entirely mechanically
- F16D43/20—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure
- F16D43/21—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure with friction members
- F16D43/211—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure with friction members with radially applied torque-limiting friction surfaces
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transmission Devices (AREA)
Abstract
The application provides an overload protection anti-slip device, which belongs to the technical field of aviation motors and comprises a small shaft, a rocker arm, a cam, a pilot assembly, a first gear, a second gear, a third gear, a fourth gear and a second pilot; the moment applied to the fourth gear is transmitted to the actuator assembly through the second actuator, the first gear, the second gear and the third gear, and when the actuator assembly rotates, the clamping ring drives the small shaft to rotate, and meanwhile, the clamping ring drives the cam to rotate. When the load is too large, the small shaft is not moved, the cam acts on the inner side of the lug of the clamping ring, and the clamping ring shrinks and slips in the first actuator. The device has small volume and light weight, can effectively and reliably realize the overload protection function, and is used for aviation motors.
Description
Technical Field
The application belongs to the technical field of aviation motors and relates to an overload protection anti-slip device.
Background
At present, the aviation rotary electric mechanism has overload use phenomena, which cause the phenomena of gear tooth breakage of a transmission part, non-operation of a motor and the like.
In order to further improve the reliability, the maintainability, the safety and the like of the product and prevent the safety accidents of the airplane caused by the overlarge load of the electric mechanism in the use process in the flying process, an overload protection device needs to be designed in the aviation electric mechanism.
Disclosure of Invention
In order to solve among the prior art the rotatory electric mechanism of aviation class and have overload use phenomenon, lead to the problem of phenomenon such as transmission part gear teeth fracture and motor inoperative, this application provides an overload protection anti-skidding device, technical scheme is as follows:
an overload protection anti-skid device comprising: the gear transmission mechanism comprises a small shaft, a rocker arm, a cam, a pilot assembly, a first gear, a second gear, a third gear, a fourth gear and a second pilot;
the rocker arm is sleeved outside the middle part of the small shaft, the small shaft is riveted with the rocker arm, and one end of the small shaft is positioned in the shell; the fourth gear and the second actuator are connected with the small shaft; the first gear is fixed in the shell at the outer part, and the inner part is meshed with the second gear and the third gear; three circular table surfaces are uniformly distributed on one side of the second actuator along the circumferential direction, each circular table surface is provided with a third gear, and the circular table surface of the second actuator is fixed with the third gear;
the guide actuator assembly comprises a clamping ring and a first guide actuator, the clamping ring is provided with two lugs, the inner diameter and the outer diameter of the clamping ring are eccentric, one side of the first guide actuator is provided with a trapezoidal groove, the clamping ring is positioned in the trapezoidal groove of the first guide actuator, the clamping ring is tightly attached to the groove wall of the trapezoidal groove of the first guide actuator, the other side of the first guide actuator is uniformly provided with three circular table surfaces along the circumferential direction, each circular table surface is provided with a second gear, and the circular table surfaces of the first guide actuator and the second gears are fixed;
the cam is arranged into a step ring structure with a fan-shaped notch, the inner diameter and the outer diameter of the cam are eccentric, a large ring surface with the fan-shaped notch is attached to the bottom surface of the shell, a small ring surface with the fan-shaped notch penetrates through the clamping ring and is coaxially installed with the clamping ring, and two lugs of the clamping ring are positioned in the fan-shaped notch of the cam and are in clearance fit;
the small shaft penetrates through the cam to be connected with the first guide actuator, a protruding structure is arranged at one end of the small shaft, the width of the protruding structure is smaller than the distance between the two lugs of the clamping ring, and the two lugs of the clamping ring are in clearance fit with the protruding structure of the small shaft;
the torque applied to the fourth gear is transmitted to the actuator assembly through the second actuator, the first gear, the second gear and the third gear; when the guide actuator assembly rotates, friction force exists between the first guide actuator and the clamping ring, the clamping ring drives the small shaft to rotate, and meanwhile the clamping ring drives the cam to rotate. When the load is too large, the small shaft is not moved, the cam acts on the inner side of the lug of the clamping ring, and the clamping ring shrinks and slips in the first actuator.
The trapezoidal groove of the first actuator is isosceles trapezoid, and the base angle is 45 degrees or 60 degrees;
the outer edge of the clamping ring is in an isosceles trapezoid shape, and the bottom angle is 45 degrees or 60 degrees;
the first guide device circular table surface and the second gear are fixed through a first gasket and a first limiting piece;
the second guide circular table surface and the third gear are fixed through a second gasket and a second limiting piece.
The first limiting piece and the second limiting piece are of T-shaped structures.
The first cylindrical pin sequentially penetrates through the fourth gear, the first actuator and the second actuator and is coaxially connected with the small shaft.
Wherein, the rocking arm passes through the second cylindric lock and cup joints in the staff middle part outside.
Wherein, the contact surface of staff and casing is provided with O type sealing washer.
And one end of the first cylindrical pin, which is far away from the small shaft, is fixedly connected with an external power device through a bushing.
Wherein, the collar is made of a material steel belt T9A, and the surface is blued.
The application provides an overload protection anti-skidding device, small, light in weight to effective, reliable realization overload protection requires. The safety accident of the airplane in the flying process caused by the overlarge load of the electric mechanism in the using process is prevented.
Drawings
Fig. 1 is a schematic structural diagram of an overload protection anti-slip device provided by the application;
fig. 2 is a schematic structural diagram of a small shaft provided in the present application.
FIG. 3 is a schematic structural view of an actuator assembly provided herein;
FIG. 4 is a schematic view of a collar provided herein;
fig. 5 is a schematic structural diagram of a cam provided in the present application.
Detailed Description
The present application is described in further detail below.
As shown in fig. 1, the present application provides an overload protection anti-slip device including: the device comprises a small shaft 1, a rocker arm 2, a cam 3, a guide actuator assembly 4, a first gear 5, a second gear 6, a third gear 9, a fourth gear 13 and a second guide actuator 14;
the rocker arm 2 is sleeved outside the middle part of the small shaft 1, the small shaft 1 is riveted with the rocker arm 2, and one end of the small shaft 1 is positioned in the shell; the fourth gear 13 and the second actuator 14 are connected with the small shaft 1; the first gear 5 is fixed in the shell at the outer part, and the inner part is meshed with the second gear 6 and the third gear 9; three circular table surfaces are uniformly distributed on one side of the second actuator 14 along the circumferential direction, each circular table surface is provided with a third gear 9, and the circular table surfaces of the second actuator 14 are fixed with the third gears 9;
as shown in fig. 3, the actuator assembly 4 includes a collar 4a and a first actuator 4b, the collar 4a is provided with two lugs 100, the inner diameter and the outer diameter of the collar 4a are eccentric, one side of the first actuator 4b is provided with a trapezoidal groove, the collar 4a is located in the trapezoidal groove of the first actuator 4b, the walls of the trapezoidal grooves of the collar 4a and the first actuator 4b are tightly attached, the other side of the first actuator 4b is uniformly distributed with three circular table surfaces along the circumferential direction, each circular table surface is provided with a second gear 6, and the circular table surface of the first actuator 4b and the second gear 6 are fixed;
the cam 3 is set to be a step ring structure with a fan-shaped notch, the inner diameter and the outer diameter of the cam 3 are eccentric, a large ring surface with the fan-shaped notch is attached to the bottom surface of the shell, a small ring surface with the fan-shaped notch penetrates through the clamping ring 4a and is coaxially installed with the clamping ring 4a, and two lugs of the clamping ring 4a are positioned in the fan-shaped notch of the cam 3 and are in clearance fit;
the small shaft 1 passes through the cam 3 to be connected with the first actuator 4b, one end of the small shaft 1 is provided with a convex structure 1a (shown in figure 2), the width of the convex structure 1a is smaller than the distance between two lugs 100 of the clamping ring 4a, and the two lugs 100 of the clamping ring 4a are in clearance fit with the convex structure 1a of the small shaft 1;
the moment applied to the fourth gear 13 is transmitted to the actuator assembly 4 through the second actuator 14, the first gear 5, the second gear 6 and the third gear 9; when the actuator assembly 4 rotates, a friction force exists between the first actuator 4b and the clamping ring 4a, the clamping ring 4a drives the small shaft 1 to rotate, and meanwhile, the clamping ring 4a drives the cam 3 to rotate. When the load is too large, the small shaft 1 is not moved, the cam 3 acts on the inner side of the lug of the clamping ring 4a, and the clamping ring 4a shrinks and slides in the first actuator 4 b.
Wherein, the trapezoid groove of the first actuator 4b is isosceles trapezoid, and the base angle can be 45 degrees or 60 degrees;
the outer edge of the clamping ring 4a is in an isosceles trapezoid shape, and the bottom angle can be 45 degrees or 60 degrees;
as shown in fig. 1, the first actuator 4b is fixed to the second gear 6 via a first washer 7 and a first stopper 8; the first washer functions to reduce the friction force of the contact end surface of the first actuator 4b and the second gear 6.
The second actuator 14 and the third gear 9 are fixed by a second washer 10 and a second stopper 11, and the first washer is used for reducing the friction force of the contact end surface of the second actuator 14 and the third gear 9.
The first stopper 8 and the second stopper 11 are of a T-shaped configuration for fastening so that the second gear 6 and the third gear 9 are reliably fixed to the circular table surfaces of the first actuator 4b and the second actuator 14, respectively.
The first cylindrical pin 15 passes through the fourth gear 13, the first actuator 4b and the second actuator 14 in sequence, and is coaxially connected with the small shaft 1.
Rocker arm 2 cup joints in the staff 1 middle part outside through second cylindric lock 17, through riveting reliable with 2 little fixed staff 1 on of rocker arm, rocker arm 2 is used for instructing output angle's position.
The contact surface of staff 1 and casing is provided with O type sealing washer 16, prevents that outside steam from getting into overload protection device through the casing, and then makes first leading ware 4b get the trapezoidal cell wall and rust with rand 4a, and when the load was too big, when the staff did not move, cam 3 acted on rand 4a lug 100 inboard, and rand 4a can not contract in first leading ware 4b and skid, can not play good overload protection requirement.
One end of the first cylindrical pin 15 far away from the small shaft 1 is fixedly connected with an external power device through a bushing 12. The external power device is mainly an electric motor, and the positive and negative rotation of the electric motor is realized by respectively supplying power to two positive outgoing lines of the electric motor. When the circuit on the airplane is connected, the gear shaft of the motor outputs rotary motion, the actuator is driven to rotate through the two-stage planetary gear train, and therefore the torque applied to the fourth gear 13 is transmitted to the actuator assembly 4 through the second actuator 14, the first gear 5, the second gear 6 and the third gear 9; when the actuator assembly 4 rotates, a friction force exists between the first actuator 4b and the clamping ring 4a, the clamping ring 4a drives the small shaft 1 to rotate, and meanwhile, the clamping ring 4a drives the cam 3 to rotate. When the load is too large, the small shaft 1 is not moved, the cam 3 acts on the inner side of the lug of the clamping ring 4a, and the clamping ring 4a shrinks and slides in the first actuator 4b, so that the overload protection requirement is realized.
The outer edge of the clamping ring 4a is in an isosceles trapezoid shape, the clamping ring is made of a steel strip T9A, the surface of the clamping ring is blue, the wear resistance is good, the abrasion loss between the clamping ring 4a and the first actuator 4b can be effectively reduced, and the groove walls of the trapezoid grooves of the clamping ring 4a and the first actuator 4b are tightly attached.
The application provides an overload protection anti-skidding device, small, light in weight to effective, reliable realization overload protection requirement prevents that electric machanism load is too big in the use and leads to the aircraft to take place the incident in flight process.
The foregoing is merely a detailed description of the embodiments of the present invention, and some of the conventional techniques are not detailed. The scope of the present invention is not limited thereto, and any changes or substitutions that can be easily made by those skilled in the art within the technical scope of the present invention will be covered by the scope of the present invention.
Claims (9)
1. An overload protection anti-slip device, comprising: the device comprises a small shaft (1), a rocker arm (2), a cam (3), a pilot assembly (4), a first gear (5), a second gear (6), a third gear (9), a fourth gear (13) and a second pilot (14);
the rocker (2) is sleeved outside the middle part of the small shaft (1), the small shaft (1) is riveted with the rocker (2), and one end of the small shaft (1) is positioned in the shell; the fourth gear (13) and the second actuator (14) are connected with the small shaft (1); the first gear (5) is fixed in the shell at the outer part, and the inner part is meshed with the second gear (6) and the third gear (9); three circular table surfaces are uniformly distributed on one side of the second actuator (14) along the circumferential direction, each circular table surface is provided with a third gear (9), and the circular table surface of the second actuator (14) is fixed with the third gear (9);
the guide actuator assembly (4) comprises a clamping ring (4a) and a first guide actuator (4b), the clamping ring (4a) is provided with two lugs (100), the inner diameter and the outer diameter of the clamping ring (4a) are eccentric, one side of the first guide actuator (4b) is provided with a trapezoidal groove, the clamping ring (4a) is located in the trapezoidal groove of the first guide actuator (4b), the clamping ring (4a) is tightly attached to the groove wall of the trapezoidal groove of the first guide actuator (4b), three circular table surfaces are uniformly distributed on the other side of the first guide actuator (4b) along the circumferential direction, each circular table surface is provided with a second gear (6), and the circular table surface of the first guide actuator (4b) is fixed to the second gear (6);
the cam (3) is arranged to be of a step ring structure with a fan-shaped notch, the inner diameter and the outer diameter of the cam (3) are eccentric, a large ring surface with the fan-shaped notch is attached to the bottom surface of the shell, a small ring surface with the fan-shaped notch penetrates through the clamping ring (4a) and is coaxially mounted with the clamping ring (4a), and two lugs of the clamping ring (4a) are located in the fan-shaped notch of the cam (3) and are in clearance fit;
the small shaft (1) penetrates through the cam (3) to be connected with the first actuator (4b), one end of the small shaft (1) is provided with a protruding structure (1a), the width of the protruding structure (1a) is smaller than the distance between the two lugs (100) of the clamping ring (4a), and the two lugs (100) of the clamping ring (4a) are in clearance fit with the protruding structure (1a) of the small shaft (1);
the moment applied to the fourth gear (13) is transmitted to the actuator assembly (4) through the second actuator (14), the first gear (5), the second gear (6) and the third gear (9); when the actuator assembly (4) rotates, friction force exists between the first actuator (4b) and the clamping ring (4a), the clamping ring (4a) drives the small shaft (1) to rotate, and meanwhile, the clamping ring (4a) drives the cam (3) to rotate; when the load is too large, the small shaft (1) is not moved, the cam (3) acts on the inner side of the lug of the clamping ring (4a), and the clamping ring (4a) shrinks and slides in the first actuator (4 b).
2. The overload protection anti-slip device according to claim 1,
the trapezoid groove of the first actuator (4b) is isosceles trapezoid, and the base angle is 45 degrees or 60 degrees;
the outer edge of the clamping ring (4a) is isosceles trapezoid, and the bottom angle is 45 degrees or 60 degrees.
3. The overload protection anti-slip device according to claim 1,
the circular table surface and the second gear (6) of the first actuator (4b) are fixed through a first gasket (7) and a first stopper (8);
the circular table surface of the second actuator (14) and the third gear (9) are fixed through a second gasket (10) and a second stopper (11).
4. The overload protection anti-slip device according to claim 3,
the first stopper (8) and the second stopper (11) are of a T-shaped structure.
5. The overload protection anti-slip device according to claim 1,
the first cylindrical pin (15) sequentially passes through the fourth gear (13), the first actuator (4b) and the second actuator (14) and is coaxially connected with the small shaft (1).
6. The overload protection anti-slip device according to claim 1,
the rocker arm (2) is sleeved outside the middle part of the small shaft (1) through a second cylindrical pin (17).
7. The overload protection anti-slip device according to claim 1,
an O-shaped sealing ring (16) is arranged on the contact surface of the small shaft (1) and the shell.
8. The overload protection anti-slip device according to claim 1,
one end of the first cylindrical pin (15) far away from the small shaft (1) is fixedly connected with an external power device through a bushing (10).
9. The overload protection anti-slip device according to claim 1,
the collar (4a) is made of a steel strip T9A.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111157811.9A CN113803383B (en) | 2021-09-30 | 2021-09-30 | Overload protection anti-slip device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111157811.9A CN113803383B (en) | 2021-09-30 | 2021-09-30 | Overload protection anti-slip device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN113803383A true CN113803383A (en) | 2021-12-17 |
| CN113803383B CN113803383B (en) | 2023-06-27 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN202111157811.9A Active CN113803383B (en) | 2021-09-30 | 2021-09-30 | Overload protection anti-slip device |
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Citations (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB224449A (en) * | 1924-03-17 | 1924-11-13 | Simon Holdener | Improvements in toothed gearing |
| JPH0979293A (en) * | 1995-09-18 | 1997-03-25 | Tsubakimoto Emason:Kk | Overload protecting mechanism |
| US5690577A (en) * | 1994-07-25 | 1997-11-25 | Ims Morat Sohne Gmbh | Gear Mechanism |
| JP2005054981A (en) * | 2004-03-19 | 2005-03-03 | Masahiro Kurita | Harmonic drive reduction gear, motor with reduction gear and driving system |
| CN101099438A (en) * | 2007-05-06 | 2008-01-09 | 宁波爱乐吉电动工具有限公司 | Pruning machine |
| US20100164312A1 (en) * | 2008-12-30 | 2010-07-01 | Hong Fu Jin Precision Industry (Shenzhen) Co.,Ltd. | Motor overload protection device |
| CN102052438A (en) * | 2010-12-27 | 2011-05-11 | 宁波划一马达有限公司 | Gear drive structure with function of overload protection |
| US20140011598A1 (en) * | 2012-07-05 | 2014-01-09 | Shanghai Kohler Electronics, Ltd. | Overload protection torque transmission device |
| CN203906699U (en) * | 2014-01-20 | 2014-10-29 | 常州天安尼康达电器有限公司 | Gear mechanism with mechanical slip protection device |
| CN105909749A (en) * | 2016-06-23 | 2016-08-31 | 苏州金莱克精密机械有限公司 | Overload protection mechanism and hedge trimmer using same |
| CN108462325A (en) * | 2018-05-03 | 2018-08-28 | 河北工业大学 | A kind of self-service obstacle crossing type overload protection arrangement |
| CN108923581A (en) * | 2018-07-11 | 2018-11-30 | 上海新世纪机器人有限公司 | The overload protection arrangement of miniature DC geared motor |
| CN112234757A (en) * | 2020-09-22 | 2021-01-15 | 兰州万里航空机电有限责任公司 | Take overload protection's electric mechanism |
| JP2021011940A (en) * | 2019-07-09 | 2021-02-04 | 日本電産サンキョー株式会社 | Overload protection mechanism and geared motor equipped with the same |
-
2021
- 2021-09-30 CN CN202111157811.9A patent/CN113803383B/en active Active
Patent Citations (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB224449A (en) * | 1924-03-17 | 1924-11-13 | Simon Holdener | Improvements in toothed gearing |
| US5690577A (en) * | 1994-07-25 | 1997-11-25 | Ims Morat Sohne Gmbh | Gear Mechanism |
| JPH0979293A (en) * | 1995-09-18 | 1997-03-25 | Tsubakimoto Emason:Kk | Overload protecting mechanism |
| JP2005054981A (en) * | 2004-03-19 | 2005-03-03 | Masahiro Kurita | Harmonic drive reduction gear, motor with reduction gear and driving system |
| CN101099438A (en) * | 2007-05-06 | 2008-01-09 | 宁波爱乐吉电动工具有限公司 | Pruning machine |
| US20100164312A1 (en) * | 2008-12-30 | 2010-07-01 | Hong Fu Jin Precision Industry (Shenzhen) Co.,Ltd. | Motor overload protection device |
| CN102052438A (en) * | 2010-12-27 | 2011-05-11 | 宁波划一马达有限公司 | Gear drive structure with function of overload protection |
| US20140011598A1 (en) * | 2012-07-05 | 2014-01-09 | Shanghai Kohler Electronics, Ltd. | Overload protection torque transmission device |
| CN203906699U (en) * | 2014-01-20 | 2014-10-29 | 常州天安尼康达电器有限公司 | Gear mechanism with mechanical slip protection device |
| CN105909749A (en) * | 2016-06-23 | 2016-08-31 | 苏州金莱克精密机械有限公司 | Overload protection mechanism and hedge trimmer using same |
| CN108462325A (en) * | 2018-05-03 | 2018-08-28 | 河北工业大学 | A kind of self-service obstacle crossing type overload protection arrangement |
| CN108923581A (en) * | 2018-07-11 | 2018-11-30 | 上海新世纪机器人有限公司 | The overload protection arrangement of miniature DC geared motor |
| JP2021011940A (en) * | 2019-07-09 | 2021-02-04 | 日本電産サンキョー株式会社 | Overload protection mechanism and geared motor equipped with the same |
| CN112234757A (en) * | 2020-09-22 | 2021-01-15 | 兰州万里航空机电有限责任公司 | Take overload protection's electric mechanism |
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|---|---|
| CN113803383B (en) | 2023-06-27 |
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