Loading moment control and self-locking device
Technical Field
The invention relates to the technical field of space mechanism transmission, in particular to a loading torque control and self-locking device which has the functions of forward loading torque control and reverse transmission self-locking.
Background
At present, in the known aerospace transmission mechanism, the application of mechanical loading torque control is less, and a friction plate type clutch is used for realizing the loading torque control in a few applications. Above-mentioned technical scheme can realize certain loading torque control, but friction disc moment fluctuation is great, and simultaneously when the reverse load grow, the clutch will skid in the reverse direction to lead to the reverse drive of driving chain, cause the position of mechanism to change, lead to mechanism's functional failure.
Disclosure of Invention
The invention provides a loading torque control and self-locking device, aiming at solving the problems that the loading torque control device in the prior art has large torque fluctuation and can not realize reverse self-locking to cause mechanism function failure. The invention relates to a device which can realize forward loading torque control and reverse transmission self-locking.
The invention relates to a loading moment control and self-locking device, which comprises: the input shaft is supported on the shell through a bearing, the output shaft is supported on the shell through a bearing, and in order to ensure the rotational stability of the input shaft and the output shaft, the end part of the output shaft is supported in the input shaft through a bearing; the spline sleeve is fixed on the input shaft through a pin and rotates together with the input shaft;
the spline shaft is meshed with the spline housing, and the spline shaft can slide relative to the spline housing along the axis of the input shaft;
the driven shaft is connected to the driven shaft through a key structure B on the output shaft;
the output gear ring is connected with the driven shaft through a key structure C on the driven shaft;
two springs are arranged between the key structure C of the driven shaft and the output gear ring;
ten driving balls are embedded in the spline housing;
ten driven balls are embedded in the driven shaft;
in the initial state, the driving balls and the driven balls are distributed along the circumferential direction in a staggered manner;
the spring is arranged between the spline sleeve and the spline shaft and used for providing initial contact force between the driving ball and the driven ball;
the duplicate gear is supported on the shell through a bearing;
the duplicate gear is respectively meshed with the bevel gear parts of the output gear ring and the worm gear;
the worm wheel is mounted on the output shaft by means of a key structure a, the worm wheel being in engagement with the worm portion of the worm gear.
After the technical scheme is adopted, the self-locking mechanism has the characteristics of forward loading torque control and reverse transmission self-locking, can stably maintain the position of the mechanism, and has the beneficial effects of simple structure, light weight and high transmission efficiency.
Drawings
FIG. 1 is a schematic view of a forward drive configuration of the present invention;
FIG. 2 is a partial cross-sectional view of the forward drive of the present invention;
FIG. 3 is a schematic view of the reverse drive configuration of the present invention;
FIG. 4 is a partial cross-sectional view of the reverse drive of the present invention;
figure 5 is a partial cross-sectional view of the ball bearing of the present invention.
In fig. 1 to 5: 1-output shaft, 2-worm gear, 3-duplicate gear, 4-bearing, 5-spline housing, 6-bearing, 7-input shaft, 8-bearing, 9-pin, 10-spring, 11-spline shaft, 12-driving ball, 13-driven ball, 14-driven shaft, 15-output gear ring, 16-worm gear, 17-shell, 18-bearing, 19-spring.
Detailed Description
Preferred embodiments of the present invention will be described below with reference to the accompanying drawings.
Fig. 1 is a schematic structural view of a forward drive of the present invention, fig. 2 is a partial sectional view of the forward drive of the present invention, and fig. 5 is a partial sectional view of a ball portion of the present invention: as shown in the embodiments shown in fig. 1, 2 and 5, the apparatus comprises: the input shaft 7 is supported on the housing 17 through the bearing 8, the output shaft 1 is supported on the housing 17 through the bearing 18, and in order to ensure the rotation stability of the input shaft 7 and the output shaft 1, the end part of the output shaft 1 is supported in the input shaft 7 through the bearing 6. The spline housing 5 is fixed to the input shaft 7 by a pin 9 and rotates together with the input shaft 7. Spline shaft 11 is engaged with spline housing 5 by a spline pair, and spline shaft 11 is slidable relative to spline housing 5 along the axis of input shaft 7. The driven shaft 14 is coupled thereto by a key structure B on the output shaft 1. The output ring gear 15 is coupled to the driven shaft 14 by a key structure C. Two springs 19 are mounted between the key structure C of the driven shaft 14 and the output ring gear 15. Ten driving balls 12 are embedded in the spline housing 11. Ten driven balls 13 are embedded in the driven shaft 14. In the initial state, the driving balls 12 and the driven balls 13 are distributed along the circumferential direction in a staggered manner. A spring 10 is installed between the spline housing 5 and the spline shaft 11 for providing an initial contact force between the driving balls 12 and the driven balls 13. The double gear 3 is supported on the housing 17 by a bearing 4. The dual gear 3 consists of a straight gear and a bevel gear, the straight gear is meshed with the output gear ring 15, and the bevel gear is meshed with the bevel gear part of the worm gear 2. The worm wheel 16 is mounted on the output shaft 1 by a key structure a, and the worm wheel 16 is engaged with the worm portion of the worm gear 2.
The operation of the present invention is described below. The description is given taking the clockwise rotation of the input shaft 7 as an example, and the counterclockwise rotation of the input shaft 7 is also applicable.
Fig. 1 is a schematic view of a forward drive structure of the present invention, fig. 2 is a partial sectional view of the forward drive structure of the present invention, and fig. 5 is a partial sectional view of a ball portion of the present invention. In the initial state, the driving balls 12 and the driven balls 13 are distributed along the circumferential direction in a staggered manner. The spring 10 presses the driving ball 12 and the driven ball 13 against each other.
When power transmission is started, the input shaft 7 rotates clockwise, the spline housing 5 is driven to rotate clockwise through the pin 9, and the spline housing 5 drives the spline shaft 11 to rotate clockwise through the spline pair. Because the driving balls 12 and the driven balls 13 are distributed along the circumferential direction in a staggered manner, and simultaneously the springs 10 enable the driving balls 12 and the driven balls 13 to generate contact pressure, power is transmitted to the driven balls 13 from the driving balls 12, so that the driven shaft 14 is driven to rotate clockwise. The driven shaft 14 transmits power to the output shaft 1 through the key structure B, so that the output shaft 1 is driven to rotate clockwise. The driven shaft 14 simultaneously transmits motion to the output gear ring 15 through the spring 19, the output gear ring 15 transmits motion to the straight gear of the dual gear 3, the bevel gear part of the dual gear 3 transmits power to the bevel gear part of the worm gear 2, so that the worm gear 2 is driven to rotate, the worm gear 2 drives the worm wheel 16 to rotate when rotating, and the worm wheel 16 is simultaneously connected to the output shaft 1 through the key structure A and synchronously rotates with the output shaft 1.
When the load on the output shaft 1 increases gradually, the power transmitted by the spring force provided by the spring 10 is not sufficient to overcome the load, and the output shaft 1 will not rotate. The input shaft 7 continues to rotate, the passive balls 13 will press the active balls 12, forcing the active balls 12 to move backward, and the active balls 12 will push the spline shaft 11 to move backward along the axis of the input shaft 7. When the active ball 12 crosses the passive ball 13, the active ball 12 will be reset by the spring 10 and then contact the next passive ball 13, so that the input shaft 7 will slip relative to the output shaft 1 and generate a continuous torque on the output shaft 1, and the torque applied to the output shaft 1 can be controlled by adjusting the magnitude of the spring force of the spring 10.
When the invention transmits power in the forward direction, because the key structure C of the driven shaft 14 and the output gear ring 15 are provided with the spring 19, and the spring force of the spring 19 is very small, the invention can ensure that the power of the input shaft 7 is transmitted to the output shaft 1 through the driven shaft 14, and the driven shaft 14 only transmits motion but not power to the output gear ring 15, thereby avoiding the problem of low transmission efficiency when the worm gear pair transmits power in the forward direction.
Fig. 3 is a schematic view of a reverse drive structure of the present invention, and fig. 4 is a partial sectional view of the reverse drive structure of the present invention. When the input shaft 7 slips relative to the output shaft 1, indicating that the torque applied to the output shaft 1 reaches the set value, the input shaft 7 stops rotating. When the load of the output shaft 1 becomes large, the output shaft 1 will have a tendency to rotate in the reverse direction, and the load of the output shaft 1 is transmitted to the worm wheel 16 through the key structure a. Due to the self-locking effect of the worm wheel 16 and the worm gear pair of the worm gear 2, the output shaft 1 will not rotate. It is thereby achieved that the position is maintained even when the load on the output shaft 1 becomes large without the occurrence of reverse rotation leading to mechanism malfunction.
As shown above, the invention has the characteristics of forward loading torque control and reverse transmission self-locking, can stably maintain the position of the mechanism, and has the advantages of simple structure, light weight and high transmission efficiency.
While the invention will be described in connection with only one preferred embodiment, it will be understood that it is not intended to limit the invention to that embodiment. On the contrary, the invention is intended to cover all alternatives, modifications and equivalents, which may be included within the spirit and scope of the invention as defined by the appended claims.