CN216478705U

CN216478705U - Gear mechanism for rotary driving device

Info

Publication number: CN216478705U
Application number: CN202120944366.XU
Authority: CN
Inventors: 周志坚; 段悠扬
Original assignee: Hefei Bolin Advanced Materials Co ltd
Current assignee: Hefei Bolin Advanced Materials Co ltd
Priority date: 2021-04-30
Filing date: 2021-04-30
Publication date: 2022-05-10
Anticipated expiration: 2031-04-30

Abstract

The utility model discloses a gear mechanism for a rotary driving device, which comprises an external gear and two hollow truncated cones, wherein the two truncated cones are arranged in an inner ring of the external gear, and the smaller end surfaces of the two truncated cones are arranged oppositely; the frustum body is sleeved on the periphery of the connecting shaft and meshed with the connecting shaft; the taper of the truncated cone is tan 6-tan 30 degrees. The taper of the truncated cone is set at tan 6-tan 30 degrees, and the adjustment sensitivity of the safety clutch is ensured.

Description

Gear mechanism for rotary driving device

Technical Field

The utility model relates to the technical field of rotary driving equipment, in particular to a gear mechanism for a rotary driving device.

Background

The traditional rotary driving device is generally composed of a worm, a rotary support, a shell, a motor and the like, the motor is used as a driving source and connected with the worm, and the worm rotates to drive the meshed rotary support to rotate, so that the rotary driving device can bear axial force, radial force and tipping moment.

In order to avoid damage to a motor and a device when an external load exceeds the rated load of the rotary driving device, the rotary driving device capable of adjusting torque is available on the market, a safety clutch is arranged in the rotary driving device, the device and the motor can be protected, and when the external load exceeds the rated load of the rotary driving device, the safety clutch realizes self protection by relative sliding. When the torque transmitted to the safety clutch reaches a certain determined value (namely, the slipping torque), the automatic separation can be realized, the size of the slipping torque is mainly controlled by the depth of an adjusting bolt, and the slipping torque can be changed when the adjusting bolt rotates for a certain angle; when the rotation angle is fixed, the larger the change range of the slip torque is, the more sensitive the adjusting bolt is. The sensitivity of the adjusting bolt is related to the overall performance of the entire safety clutch.

SUMMERY OF THE UTILITY MODEL

The present invention is directed to a gear mechanism for a slewing drive device, which solves the problems of the related art described above, and can ensure high sensitivity of slip torque adjustment of a safety clutch by improving the structure of the gear mechanism.

In order to achieve the purpose, the utility model provides the following technical scheme:

a gear mechanism for a rotary driving device comprises an external gear and two hollow truncated cones, wherein the two truncated cones are arranged in an inner ring of the external gear, and the smaller end surfaces of the two truncated cones are arranged opposite to each other; the truncated cone is sleeved on the periphery of the connecting shaft and meshed with the connecting shaft; the taper of the truncated cone is tan 6-tan 30 degrees.

As a further scheme of the utility model: an annular groove is formed in the larger end face of the truncated cone body, and a disc spring is arranged in the annular groove.

As a further scheme of the utility model: one end of the connecting shaft is coaxially provided with a pressing piece.

As a further scheme of the utility model: and a bearing is sleeved on the connecting shaft between the disc spring and the pressing piece.

As a further scheme of the utility model: the pressing piece is an adjusting bolt.

Compared with the prior art, the utility model has the beneficial effects that: the taper of the truncated cone is set to tan 6-tan 30 degrees, so that the adjustment sensitivity of the safety clutch is ensured. When the taper is smaller than tan6 degrees, the truncated cone and the gear are contacted to form a similar self-locking mode in the stress process, and the slip torque cannot be adjusted; when the taper is larger than tan30 degrees, the rated slip torque of the product can be achieved only by an abnormally large external force, the sensitivity is extremely low when the slip torque is adjusted, and the self structure of the safety clutch has a fracture risk. The annular groove formed in the larger end face of the truncated cone limits the disc spring, so that the disc spring can be uniformly applied to the truncated cone, and the stability of the structure is facilitated. The disc spring can bear great load in a small space, and compared with a common spring, the disc spring has larger deformation energy per unit volume and better buffering and shock absorption capacity.

Drawings

FIG. 1 is a schematic structural view of the present invention;

FIG. 2 is a side cross-sectional view of the present invention mounted on a connecting shaft;

FIG. 3 is a schematic perspective view of a truncated cone according to the present invention;

FIG. 4 is a general assembly view of the present invention in a swing drive;

in the figure: 1-shell, 2-connecting shaft, 3-worm, 4-external gear, 5-truncated cone, 51-annular groove, 6-disc spring, 7-adjusting bolt and 8-bearing.

Detailed Description

The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.

The rotation driving device comprises a shell 1 and a safety clutch arranged in the shell 1, wherein the safety clutch comprises a connecting shaft 2, a gear mechanism and a worm 3, one end of the connecting shaft 2 is arranged in the shell 1, and the other end of the connecting shaft extends out of the shell 1; the gear mechanism is sleeved on the periphery of the connecting shaft 2, the adjusting bolt transmits force to the truncated cones 5 through the disc springs 6 and the bearings 8, and when the disc springs 6 on the two sides are compressed, the distance between the two truncated cones 5 tends to be smaller, namely the distance between the two first end faces tends to be closer, so that the acting force between the truncated cones 5 and the outer gear 4 tends to be larger. The worm 3 is meshed with the outer gear ring of the outer gear 4, and the worm 3 is perpendicular to the connecting shaft 2. The worm 3 is connected with a motor, the motor drives the worm 3 to rotate, the worm 3 drives the external gear 4 meshed with the worm to rotate, the external gear 4 drives the truncated cone 5 to rotate through the acting force between the external gear 4 and the truncated cone 5, and the truncated cone 5 drives the connecting shaft 2 meshed with the truncated cone 5 to rotate. The depth of the bearing 8 is adjusted by adjusting the depth of the adjusting bolt, so that the elastic deformation of the disc springs 6 on two sides is changed, the acting force between the truncated cone 5 and the outer gear 4 is changed, and the corresponding slip torque is generated at the same time, so that the purpose of changing the output torque of the connecting shaft 2 is achieved.

In embodiment 1, as shown in fig. 1 to 4, a gear mechanism for a slewing drive device includes an external gear 4 and two hollow truncated cones 5, the truncated cones 5 having a first end surface and a second end surface, the first end surface having an outer diameter smaller than that of the second end surface, the two truncated cones 5 being built into an inner ring of the external gear 4, and the two first end surfaces being disposed opposite to each other; the truncated cone 5 is sleeved on the connecting shaft for 2 circles and meshed with the connecting shaft; the taper of the truncated cone 5 is tan6 °. The second end face of the truncated cone 5 is provided with an annular groove 51, and a disc spring 6 is arranged in the annular groove 51. One end of the connecting shaft 2 is coaxially provided with a pressing piece 7, and the pressing piece 7 is set to be an adjusting bolt. And a bearing 8 is sleeved on the connecting shaft 2 between the disc spring 6 and the pressing piece 7.

In example 2, the taper of the truncated cone 5 is tan16 ° in a gear mechanism for a rotary drive device, and the rest of the arrangement is the same as that in example 1.

In example 3, a gear mechanism for a slewing drive device, the taper of the truncated cone 5 was tan30 °, and the rest of the arrangement was the same as in example 1.

Comparative example 1, a gear mechanism for a rotary drive apparatus, the taper of the truncated cone 5 was tan40 °, and the rest of the arrangement was the same as in example 1.

In comparative example 2, in a gear mechanism for a rotary drive apparatus, the taper of the truncated cone 5 was tan3 °, and the rest of the arrangement was the same as that of example 1.

When the adjusting bolt is rotated by the same angle, the larger the change value of the output torque, the higher the sensitivity of the adjusting bolt is, and the larger the adjustable range of the slip torque is. The sensitivity of the safety clutch can therefore be characterized by testing the magnitude of the slip torque of the gear mechanism in examples 1-3 and comparative examples 1-2 at the same angle of rotation of the adjuster bolt.

The gear mechanisms in examples 1 to 3 and comparative examples 1 to 2 were sequentially assembled in the same rotary drive device (the assembly structure is shown in fig. 4), and the sensitivity test of the adjusting bolt was performed in sequence by the following test method:

1) the initial position of the adjusting bolt is marked, and the slip torque value at the initial position is recorded as 0.

2) The adjusting bolt was rotated clockwise three times, each time through 60 °.

3) The slip torque values for each of the steps 2) were recorded and calculated and the test results are summarized in table 1.

4) And rotating the adjusting bolt counterclockwise 3 times in sequence at the final position of the adjusting bolt in the step 3), wherein the rotating angle is 60 degrees each time.

5) The slip torque values for each of the steps 4) were recorded and calculated and the test results are summarized in table 1.

TABLE 1 test results

From the data in table 1, the adjusting bolt of examples 1-3 has a significantly higher adjusting sensitivity than that of comparative example 2, whereas the adjusting bolt of comparative example 1, when rotated clockwise, forms a self-locking mode when rotated counterclockwise, although having a higher adjusting sensitivity than that of examples 1-3. It is stated that within a certain range, the sensitivity of the adjusting bolt is inversely related to the taper of the truncated cone 5, and the greater the taper, the lower the sensitivity of the adjusting bolt. However, in practice, it is not preferable that the taper is as small as possible, and if the taper is too small (i.e., the frustum 5 is closer to a cylinder), it is easy to form a self-locking mode, i.e., the two frustums 5 are hard to separate after being compressed. The adjusting bolt acts on the disc spring 6, and the disc spring 6 acts on the truncated cone 5 to change the distance between the two truncated cones 5, and the distance is related to the acting force between the truncated cone 5 and the external gear 4, so that the magnitude of the slip torque is determined. If the taper of the truncated cone 5 is too large, namely greater than tan30 degrees, the sensitivity of the adjusting bolt is correspondingly reduced; the self-locking mode is easily formed if the taper of the truncated cone 5 is too small, i.e. less than tan6 °.

Although the present description is described in terms of embodiments, not every embodiment includes only a single embodiment, and such description is for clarity only, and those skilled in the art should be able to integrate the description as a whole, and the embodiments can be appropriately combined to form other embodiments as will be understood by those skilled in the art.

Therefore, the above description is only a preferred embodiment of the present application, and is not intended to limit the scope of the present application; all changes which come within the meaning and range of equivalency of the claims are to be embraced within their scope.

Claims

1. A gear mechanism for a rotary driving device comprises an external gear (4) and two hollow truncated cones (5), and is characterized in that the two truncated cones (5) are arranged in an inner ring of the external gear (4), and the smaller end faces of the two truncated cones (5) are arranged opposite to each other; the truncated cone body (5) is sleeved on the periphery of the connecting shaft (2) and meshed with the connecting shaft; the taper of the truncated cone (5) is tan 6-tan 30 degrees.

2. A gear mechanism for a rotary drive unit according to claim 1, wherein the truncated cone (5) has an annular groove (51) formed in a larger end surface thereof, and the annular groove (51) has a disc spring (6) disposed therein.

3. A gear mechanism for a rotary drive apparatus as claimed in claim 2, wherein the connecting shaft (2) is provided coaxially with a pressing member (7) at one end thereof.

4. A gear mechanism for a rotary drive apparatus as claimed in claim 3, characterized in that a bearing (8) is provided on the connecting shaft (2) between the disc spring (6) and the pressing member (7).

5. A gear mechanism for a rotary drive as claimed in claim 3, characterised in that the pressing member (7) is an adjusting bolt.