CN110332258B - Friction damping and driving limit actuator - Google Patents
Friction damping and driving limit actuator Download PDFInfo
- Publication number
- CN110332258B CN110332258B CN201910635788.6A CN201910635788A CN110332258B CN 110332258 B CN110332258 B CN 110332258B CN 201910635788 A CN201910635788 A CN 201910635788A CN 110332258 B CN110332258 B CN 110332258B
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- damping
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- locking
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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
- F16D49/00—Brakes with a braking member co-operating with the periphery of a drum, wheel-rim, or the like
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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
- F16D65/00—Parts or details
- F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
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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
- F16D2121/00—Type of actuator operation force
- F16D2121/18—Electric or magnetic
- F16D2121/20—Electric or magnetic using electromagnets
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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
- F16D2127/00—Auxiliary mechanisms
- F16D2127/06—Locking mechanisms, e.g. acting on actuators, on release mechanisms or on force transmission mechanisms
Abstract
The invention discloses a friction damping and driving limit actuator, which comprises a damping/driving device, a friction damping device, a limit locking/unlocking device and a rotating assembly which is arranged in the damping/driving device, the friction damping device and the limit locking/unlocking device in a penetrating way; the limiting locking/unlocking device comprises a limiting small ball and a limiting mechanism; the limiting small ball and the limiting mechanism are mutually attracted or repelled to realize locking or unlocking. Compared with the prior art, the invention has the following beneficial effects: the electromagnetic damping device can realize a series of actions such as high-efficiency braking, locking, unlocking and driving on an executed part, can generate ideal braking effects on high-speed braking and low-speed braking at the same time, can efficiently utilize electric energy converted in the electromagnetic damping action process to carry out electromagnetic driving, and realizes energy reutilization.
Description
Technical Field
The invention relates to an electromagnetic and friction damping buffer device, in particular to a novel electromagnetic friction damping and driving limiting actuator, wherein the buffer braking is the most common unsteady working condition in the mechanical field, the buffer braking performance is very important in connection with a braking device, and both the electromagnetic damping and the friction damping can be used for mechanism safety braking.
Background
According to the law of electromagnetic induction, when a magnetic rod enters a coil, an induced electric field is generated, the magnetic field always hinders the relative motion of the magnetic rod, and a braking force is formed on the magnetic rod, and the phenomenon is called electromagnetic damping. The electromagnetic brake manufactured according to the electromagnetic damping principle has the advantages of simple structure, controllable braking force, no contact between a primary and a secondary and the like. Therefore, the method is widely applied to the engineering fields of space butt joint, high-speed rail braking and the like. In the process of generating the electromagnetic damping force, no material is abraded or damaged, and the consumed kinetic energy can be converted into electric energy along with the generation of induced electromotive force during braking, and then the electric energy is stored by using an energy storage device, so that the energy can be recycled. However, the electromagnetic damping is greatly influenced by the speed of the braked member, and for the high-speed braked member, the coil can instantly generate a larger induced electric field and induced electromotive force, so that a good braking effect is achieved; and the electromagnetic braking effect of the braked member at lower speed is greatly reduced. The composite damper based on electromagnetism and friction can effectively make up the deficiency of the electromagnetic damper, and can coordinately distribute the action ratio of the electromagnetic damping and the friction damping: when the actuator enters the coil at a high speed, the electromagnetic damping device can remarkably consume most of kinetic energy and convert the kinetic energy into electric energy for storage, so that the burden of a friction energy consumption device is effectively reduced, and the abrasion and the damage of a friction pair interface are reduced; when the actuator enters the coil at low speed, the electromagnetic damping device has small effect, the braking is mainly completed by the friction damping device, and at the moment, the sliding friction damping can efficiently perform braking action and quickly convert kinetic energy into internal energy because the speed is small and the friction damping force is completely irrelevant to the speed. Due to the smaller speed, the relative sliding distance is shorter, so that the wear caused by friction is smaller.
The operating principle of the eddy current retarder can be expressed as that a stator coil is electrified to generate a magnetic field, a rotor rotates along with a transmission shaft, and the rotor cuts magnetic lines generated by the stator at the moment, so that eddy-shaped induced current is generated in a rotor disc. Thus, the stator applies an electromagnetic force to the rotor to hinder the rotation of the rotor, thereby generating a braking torque. Meanwhile, the eddy current circulates in the rotor disc with a certain resistance, and the electric energy is converted into heat energy due to the heat effect of the resistance, so that the mechanical energy to be consumed during buffering can be finally converted into heat energy to be dissipated. The eddy current braking effect is very obvious in high speed and short time, and the transient braking torque is large, so that the eddy current braking device has a very beneficial effect on the sudden stop braking of the medium-high speed transmission shaft.
Frictional damping is a relatively traditional mechanical braking principle, and mechanical energy is converted into internal energy by applying work through frictional resistance of a contact surface. The friction damper has the characteristics of simple structure, strong energy consumption capability, no influence of load frequency and the like, and is widely applied to the field of mechanical engineering. Since friction and frequency are independent of velocity, a friction damper is a special type of damper that is highly dependent on displacement. Since friction energy is mainly attached to two states of sliding in work, the energy-consuming braking effect of the friction energy is mainly determined by the normal pressure and the friction coefficient of a contact surface. The damper exhibits a stationary state when the external load is less than the maximum static friction force of the damper, and exhibits a sliding state once the external load is greater than the maximum static friction force of the damper. The reasonable design of the friction braking device is very critical, the contact surface of the existing viscoelastic friction damper is large, mainly surface contact is used as a main part, the normal total pressure is generated to be small, and the surface contact friction coefficient is small, so that the ideal friction damping effect is hardly obtained. The friction damping device in multi-spherical-point contact can generate great normal pressure, and the Hertz contact pressure generated by the elliptic contact (main form of point contact) can reach more than GPa, so that higher shearing force is formed, and a larger friction coefficient is generated; eventually the frictional damping effect can be significantly amplified. The existing limiting locking/unlocking device has more types, but has single function, and can rarely realize limiting locking and unlocking driving.
The electromagnetic energy collection technology converts vibration energy into electric energy by utilizing the principle of electromagnetic induction. Relative motion is generated between the coil and the magnet, so that magnetic flux in the coil is changed, and according to Faraday's law of electromagnetic induction, induced electromotive force is generated in the loop coil due to the change of the magnetic flux, and then current is generated, so that vibration energy is converted into electric energy. The electromagnetic vibration energy collecting device is divided into two types according to different relative motion forms between the coil and the magnet: one is linear and the other is rotational. The linear electromagnetic energy collection is that linear reciprocating relative motion occurs between a coil and a permanent magnet, and the magnetic flux is changed to realize energy conversion; the rotational type electromagnetic energy collection realizes energy conversion by converting vibration into rotational motion, changing magnetic flux. Because the induced electromotive force in the coil is unstable due to the unstable moving speed of the magnet, a storage battery device is needed for storing electric energy and providing electric energy for the subsequent driving action.
Disclosure of Invention
In view of the drawbacks of the prior art, the present invention provides a friction damping and driving limit actuator that solves the above-mentioned technical problems.
In order to solve the technical problem, the friction damping and driving limit actuator comprises a damping driving device, a friction damping device, a limit locking and unlocking device and a rotating assembly which is arranged in the damping driving device, the friction damping device and the limit locking and unlocking device in a penetrating manner; the limiting locking and unlocking device comprises a limiting small ball and a limiting mechanism; the limiting small ball and the limiting mechanism are mutually attracted or repelled to realize locking or unlocking.
Preferably, the limiting mechanism comprises:
the limiting sleeve is of a symmetrical conical surface structure, and the limiting small balls are arranged on the symmetrical conical surface of the limiting sleeve;
the limiting driving unit is arranged on the symmetrical conical surface of the limiting sleeve and is positioned on the outer side of the limiting small ball; the limiting small balls and the limiting driving unit are mutually attracted or repelled to realize locking or unlocking;
the rotating assembly is arranged in the limiting sleeve in a penetrating mode, and the limiting small ball is in contact with the rotating assembly.
Preferably, the friction damping means comprises:
the damping sleeve is a wedge-shaped sleeve;
a friction ball disposed on an inner wall of the damping sleeve;
the damping driving unit is arranged on the inner wall of the damping sleeve, and the friction small balls and the damping driving unit are mutually attracted or repelled to realize locking or unlocking;
the rotating assembly is arranged in the damping sleeve in a penetrating mode, and the friction ball is in contact with the rotating assembly.
Preferably, a plurality of said friction beads are distributed in equal proportion along the axial direction of said rotating assembly; the adjacent friction small balls are tangent; the inner wall of the damping sleeve and the side face of the rotating component are tangent to the friction ball.
Preferably, the relationship between the diameter of the friction ball and the inclination angle of the inner wall of the damping sleeve satisfies:
in the formula, rnThe diameter of the nth friction ball is shown, n is the number of the friction balls, and theta is the inclination angle of the inner wall of the damping sleeve.
Preferably, the damping sleeve is filled with a phase change material.
Preferably, the damping driving device includes:
the permanent magnet is wrapped on the outer side of the rotating component;
the high-turn coil is fixed on the outer side of the permanent magnet; wherein
The permanent magnets are connected in series along the axial direction of the rotating assembly in the same polarity.
Preferably, a protective sleeve is provided between the permanent magnet and the high-turn coil.
Preferably, the damping driving device includes:
the rack is arranged on the outer side of the rotating assembly along the axial direction of the rotating assembly;
the vortex retarding mechanism is meshed with the rack.
Preferably, the vortex retarding mechanism includes:
the vortex disc is in a gear shape and is meshed with the rack;
the magnetic conduction assemblies are arranged on the vortex disc; wherein
The magnetic conduction subassembly includes:
the two coils are arranged on the vortex disc at intervals through magnetic conductive discs;
and two ends of the magnetic conduction shaft are respectively connected with the coils on two sides.
Compared with the prior art, the invention has the following beneficial effects: the electromagnetic damping device can realize a series of actions such as high-efficiency braking, locking, unlocking and driving on an executed part, can generate ideal braking effects on high-speed braking and low-speed braking at the same time, can efficiently utilize electric energy converted in the electromagnetic damping action process to carry out electromagnetic driving, and realizes energy reutilization.
Drawings
Other features, objects and advantages of the present invention will become more apparent upon reading of the following detailed description of non-limiting embodiments thereof, with reference to the accompanying drawings.
FIG. 1 is a schematic structural view of an embodiment of a frictional damping and driving limit actuator according to the present invention;
FIG. 2 is a schematic structural view of a second embodiment of the frictional damping and driving limit actuator of the present invention;
FIG. 3 is a schematic view of the circumferential distribution of friction beads of the friction damping and driving limit actuator of the present invention;
FIG. 4 is a schematic view of the axial distribution of friction beads of the friction damping and driving limit actuator of the present invention;
FIG. 5 is a friction ball force diagram of the friction damping and drive limit actuator of the present invention.
Detailed Description
The present invention will be described in detail with reference to specific examples. The following examples will assist those skilled in the art in further understanding the invention, but are not intended to limit the invention in any way. It should be noted that it would be obvious to those skilled in the art that various changes and modifications can be made without departing from the spirit of the invention. All falling within the scope of the present invention.
The invention adopts the composite damping brake combining electromagnetic damping and friction damping, and realizes braking and self-driving by utilizing the energy conversion rule and the electric energy generated by the electromagnetic coil through the storage battery storage technology. The electromagnetic friction damping composite braking design can effectively brake a high-speed working component and a low-speed working component, keeps the safety and reliability of the damping device, can realize repeated use, and has longer service life than a single electromagnetic damping device and a single friction damping device.
Referring to fig. 1 to 5, fig. 1 is a schematic diagram illustrating a structure and a principle of a friction damping and driving limit actuator according to the present invention. As shown in fig. 1, the friction damping and drive limit actuator comprises three major parts: electromagnetic force damping/driving device, friction damping device, spacing locking/unlocking device. Wherein the electromagnetic damping/driving device comprises: a permanent magnet and a high turn coil; the friction damping device includes: a wedge-shaped damping sleeve, a friction ball and a damping driving unit (an elastic or permanent magnet/electromagnetic driving unit); the limit locking/unlocking device comprises: a limit ball and a limit driving unit (an elastic or permanent magnet/electromagnetic driving unit).
The invention adopts the composite damping brake combining electromagnetic damping and friction damping, and realizes braking and self-driving by utilizing the energy conversion rule and the electric energy generated by the electromagnetic coil through the storage battery storage technology. The invention can efficiently utilize the electric energy generated by electromagnetic induction and effectively reduce the sliding distance between the friction ball and the side surface of the supporting shaft, thereby reducing the abrasion volume and the abrasion depth.
The principle of the friction damping buffer limit actuator in the invention is explained by combining with figures 1, 3, 4 and 5. As shown in fig. 1, the permanent magnet 101 disposed in the outer sleeve 109 is circumferentially fixed to a support shaft 104 in a rotating assembly (including the support shaft 104, the inner rotating shaft 105, the mounting key 106, and the rotating motor 107), and the permanent magnet 101 is externally surrounded by a protective sleeve 103, and is fixedly connected to the support shaft 104 to form a damper mover mechanism, and is connected in series with the same polarity in the axial direction of the support shaft 104. The high-turn coil 102 is externally connected with a load to form a closed loop. The friction damping device includes a damping drive unit 113, a friction ball 114, and a damping sleeve 115. The limit locking/unlocking device comprises a limit sleeve 111, a limit ball 112 and a limit driving unit 110. The rotor moves along any one direction, the permanent magnet 101 and the high-turn coil 102 move relatively, and the high-turn coil 102 cuts the magnetic force line of the permanent magnet 101. When the permanent magnet 101 approaches to the high-turn coil 102 to enter, the magnetic flux of the high-turn coil 102 cutting the permanent magnet 101 is increased, and the high-turn coil 102 generates an induced potential and generates an induced current through a closed loop to further generate an induced magnetic field, wherein the direction of the induced current is opposite to that of the magnetic field of the permanent magnet 1, and the induced magnetic field represents electromagnetic resistance to the permanent magnet 101; when the permanent magnet 101 leaves the high-turn coil 102, the original magnetic flux is reduced, the direction of the magnetic field generated by the induced current is the same as the direction of the magnetic field of the permanent magnet 101, and the permanent magnet 101 is expressed as electromagnetic attraction. In both cases, the direction of the electromagnetic force is opposite to the movement direction, and the macroscopic representation shows the electromagnetic damping effect. The permanent magnet 1 and the high-turn coil 102 are in linear array, and the electromagnetic damping is in a superposition rule. Meanwhile, a displacement monitor 108 is installed in the outer sleeve 109 for real-time monitoring and feedback.
As shown in fig. 3, 4 and 5, the optimal friction balls (114, 214) in the friction damping device are arranged in such a way that the friction balls are tangent to each other in the axial direction and are distributed in the circumferential direction in an equal number. The angle of inclination of the diameter of the friction ball (114, 214) to the inner wall of the damping sleeve (115, 215)θThe relationship between them satisfies:
in the formula (I), the compound is shown in the specification,
is the diameter of the nth friction ball (114, 214), n is the number of friction balls (114, 214), and θ is the angle of inclination of the inner wall of the damping sleeve (115, 215). The total frictional heat and frictional resistance generated by the friction balls (114, 214) and the side surfaces of the support shafts (104, 208) can be obtained by the equations (1) and (2).
Formula (1):
formula (2):
wherein the parameters are pre-thrust, wedge angle, friction coefficient of the side surface of the friction ball (114, 214) and the supporting shaft (104, 208), maximum radius of the friction ball (114, 214), diameter of the supporting shaft (104, 208), radius of the minimum friction ball (114, 214), mass of the maximum friction ball (114, 214) and sliding distance. When the supporting shaft (104, 208) just enters the high-turn coil, the supporting shaft (104, 208) and the friction ball (114, 214) generate normal acting force and friction force, and in order to keep the friction ball (114, 214) and the supporting shaft (104, 208) always sliding purely, the friction ball (114, 214) is required not to spin, namely, the wedge-shaped inner wall of the damping sleeve (115, 215) tangent to the friction ball (114, 214) must be rough, so that the sliding friction force of the friction ball (114, 214) and the supporting shaft (104, 208) is smaller than the static friction force of the friction ball (114, 214) and the wedge-shaped inner wall of the damping sleeve (115, 215), and thus the friction ball (114, 214) can be ensured to only slide purely, and the maximum friction damping is realized. When the friction damping device reduces the kinetic energy to a safe locking value, the acting force direction of a limiting driving unit in the limiting locking/unlocking device is changed, meanwhile, the limiting small balls move oppositely to form extrusion, and the limiting small balls which work in the electromagnetic damping and friction damping device are in a mutually attracting state with the limiting driving unit so as to ensure that the locking is not carried out.
The principle of the eddy current friction damping buffer limit actuator in the invention is explained by combining with fig. 2, fig. 3, fig. 4 and fig. 5. As shown in fig. 2, in operation, the support shaft 208, the inner rotary shaft 216, and the rotary electric machine 212 as a whole remain stationary; the outer sleeve 201, the eddy current retarding mechanism 202, the friction damping device 203, and the limit locking/unlocking device 205 move downward as a whole. The rack 207 is provided with connecting rings (204, 206), during the movement, the rack 207 is meshed to move to convert the linear motion into the rotary motion to be transmitted to the vortex disc 217, and the electrified coil 218 generates damping torque on the vortex disc, so that the movement of the supporting shaft 208 is restrained; the small ball in the friction damping device 203 generates friction damping, and the limiting locking/unlocking device 205 locks the moving shaft when the movement is completed. The limit locking/unlocking device 205, the rotating motor 212 works to rotate the inner rotating shaft 216, and due to the constraint of the bottom end of the inner rotating shaft 216, the inner rotating shaft 216 reacts on the supporting shaft 208 to enable the supporting shaft 208 to move upwards (the supporting shaft 208 is in threaded fit with the inner rotating shaft 216, a limit groove is formed in the supporting shaft 208, and the motor is provided with a boss to ensure that the motor does not rotate along with the supporting shaft 208). Meanwhile, alternating current can be loaded through the eddy current retarding mechanism 202 and the coils 218 (the coils 218 are connected through the iron core magnetic conduction shaft 219 and are externally provided with the magnetic conduction disc 221), so that the eddy current disc 217 generates an active torque and the transmission supporting shaft 208 moves upwards. The movement process of the supporting shaft 208 can be monitored in real time through the grating speed measuring device 220 on the transmission vortex disc 217.
The friction damping device 203 includes a damping sleeve 215, a friction ball 214, and a damping driving unit 213. The working principle is the same as that of the first embodiment.
The working principle of the limit locking/unlocking device 205 can be expressed as follows: when the supporting shaft 208 is in a buffering stage, the limiting small balls 210 on the symmetrical conical surface of the limiting sleeve 211 are in an unlocking state under the action of the tension of the limiting driving unit 209; when the supporting shaft 208 finishes buffering, the limiting small balls 210 are in a locking state under the thrust action of the limiting driving unit 209. When the reverse driving is required to be started, the limiting small ball 210 on the right side of the symmetrical conical surface is completely unlocked, and the limiting small ball 210 on the left side is under the action of small thrust of the limiting driving unit 209 to ensure that the supporting shaft can be safely self-locked when the driving process slips backwards.
The novel electromagnetic friction damping and driving limiting actuator principle and the structure scheme provided in the embodiment can realize the complementary braking of the advantages of the composite damping combining the electromagnetic damping and the friction damping, and the braking and the self-driving are realized by utilizing the energy conversion rule and the electric energy generated by the electromagnetic coil through the storage battery storage technology. The electromagnetic friction damping composite braking design can effectively brake a high-speed working component and a low-speed working component at the same time, keeps the safety and reliability of the damping device, can realize repeated use, and has longer service life than a single electromagnetic damping device and a single friction damping device. The electromagnetic friction composite damping braking technology can greatly reduce the number of permanent magnets and the total acting stroke, thereby obviously reducing the total weight, achieving the lightweight design requirement and simultaneously keeping higher braking force and energy conversion efficiency.
The foregoing description of specific embodiments of the present invention has been presented. It is to be understood that the present invention is not limited to the specific embodiments described above, and that various changes or modifications may be made by one skilled in the art within the scope of the appended claims without departing from the spirit of the invention. The embodiments and features of the embodiments of the present application may be combined with each other arbitrarily without conflict.
Claims (9)
1. A friction damping and driving limit actuator is characterized by comprising a damping driving device, a friction damping device, a limit locking and unlocking device and a rotating assembly which is arranged in the damping driving device, the friction damping device and the limit locking and unlocking device in a penetrating manner; wherein
The limiting locking and unlocking device comprises a limiting small ball and a limiting mechanism; the limiting small ball and the limiting mechanism are mutually attracted or mutually repelled to realize locking or unlocking;
the stop gear includes:
the limiting sleeve is of a symmetrical conical surface structure, and the limiting small balls are arranged on the symmetrical conical surface of the limiting sleeve;
the limiting driving unit is arranged on the symmetrical conical surface of the limiting sleeve and is positioned on the outer side of the limiting small ball; the limiting small balls and the limiting driving unit are mutually attracted or repelled to realize locking or unlocking;
the rotating assembly is arranged in the limiting sleeve in a penetrating mode, and the limiting small ball is in contact with the rotating assembly.
2. The friction damping and drive limit actuator of claim 1, wherein the friction damping means comprises:
the damping sleeve is a wedge-shaped sleeve;
a friction ball disposed on an inner wall of the damping sleeve;
the damping driving unit is arranged on the inner wall of the damping sleeve, and the friction small balls and the damping driving unit are mutually attracted or repelled to realize locking or unlocking;
the rotating assembly is arranged in the damping sleeve in a penetrating mode, and the friction ball is in contact with the rotating assembly.
3. The friction damping and drive limit actuator of claim 2, wherein a plurality of the friction balls are distributed in equal proportion along an axial direction of the rotating assembly; the adjacent friction small balls are tangent; the inner wall of the damping sleeve and the side face of the rotating component are tangent to the friction ball.
4. The frictional damping and drive limit actuator of claim 3, wherein the relationship between the diameter of the friction ball and the angle of inclination of the damping sleeve inner wall satisfies:
in the formula, rnThe diameter of the nth friction ball is shown, n is the number of the friction balls, and theta is the inclination angle of the inner wall of the damping sleeve.
5. The frictional damping and drive limit actuator of claim 2, wherein a phase change material is filled within the damping sleeve.
6. The frictional damping and drive limit actuator of claim 1, wherein the damping drive comprises:
the permanent magnet is wrapped on the outer side of the rotating component;
the high-turn coil is fixed on the outer side of the permanent magnet; wherein
The permanent magnets are connected in series along the axial direction of the rotating assembly in the same polarity.
7. The frictional damping and drive limit actuator of claim 6, wherein a protective sheath is disposed between the permanent magnet and the high-turn coil.
8. The frictional damping and drive limit actuator of claim 1, wherein the damping drive comprises:
the rack is arranged on the outer side of the rotating assembly along the axial direction of the rotating assembly;
the vortex retarding mechanism is meshed with the rack.
9. The friction damping and drive limit actuator of claim 8, wherein the eddy current retarding mechanism comprises:
the vortex disc is in a gear shape and is meshed with the rack;
the magnetic conduction assemblies are arranged on the vortex disc; wherein
The magnetic conduction subassembly includes:
the two coils are arranged on the vortex disc at intervals through magnetic conductive discs;
and two ends of the magnetic conduction shaft are respectively connected with the coils on two sides.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201910635788.6A CN110332258B (en) | 2019-07-15 | 2019-07-15 | Friction damping and driving limit actuator |
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| CN201910635788.6A CN110332258B (en) | 2019-07-15 | 2019-07-15 | Friction damping and driving limit actuator |
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| CN110332258B true CN110332258B (en) | 2020-09-15 |
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Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104235235A (en) * | 2014-09-16 | 2014-12-24 | 江苏理工学院 | Vehicle hub-type integrated hydraulic retardance and friction brake device |
| US20150075149A1 (en) * | 2013-09-17 | 2015-03-19 | Airbus Helicopters Deutschland GmbH | Flexible response secured mechanical balancing for multiple control actuators with a common output |
| CN205429962U (en) * | 2015-11-25 | 2016-08-03 | 杨斌堂 | Bistable state actuator of rotation mode |
| CN107989928A (en) * | 2017-10-30 | 2018-05-04 | 河北汉光重工有限责任公司 | A kind of damping brake device |
| CN108223663A (en) * | 2016-12-14 | 2018-06-29 | 苏斯帕有限公司 | Rubbing device and the frcition damper with the type rubbing device |
-
2019
- 2019-07-15 CN CN201910635788.6A patent/CN110332258B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20150075149A1 (en) * | 2013-09-17 | 2015-03-19 | Airbus Helicopters Deutschland GmbH | Flexible response secured mechanical balancing for multiple control actuators with a common output |
| CN104235235A (en) * | 2014-09-16 | 2014-12-24 | 江苏理工学院 | Vehicle hub-type integrated hydraulic retardance and friction brake device |
| CN205429962U (en) * | 2015-11-25 | 2016-08-03 | 杨斌堂 | Bistable state actuator of rotation mode |
| CN108223663A (en) * | 2016-12-14 | 2018-06-29 | 苏斯帕有限公司 | Rubbing device and the frcition damper with the type rubbing device |
| CN107989928A (en) * | 2017-10-30 | 2018-05-04 | 河北汉光重工有限责任公司 | A kind of damping brake device |
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