Patent Application
20240093771
The disclosure relates to a method for designing a tooth profile of a cycloidal gear of a gear shift actuator used in an automobile or the like.
In general, the theoretical design method of cycloidal gears is based on zero backlash of inner tooth gears and outer tooth gears, so if precise machining is not accompanied, cycloidal gears may not be smoothly driven and noise and durability may be adversely affected, and therefore, precise machining is required.
Referring to
Alternatively, in the related art, as shown in
However, as in the related art, the power transmission efficiency may be increased by changing the eccentric amount or changing the outer diameter shape of the outer tooth gear to which an arbitrary formula is applied, but the design thereof deviates from the general rolling circle design of cycloidal gears, and thus, it is necessary to machine a shape of an arbitrary outer tooth gear, not an arc shape, using the general cycloidal gear machining method. Therefore, since a desired machining precision may not be obtained to lower machining precision, resulting in increased noise during operation and reduced durability.
The disclosure provides a method for designing a tooth profile of a cycloidal gear of a gear shift actuator, capable of providing a backlash through a change in a rolling circle radius of a tooth profile of an inner tooth gear or an outer tooth gear of cycloidal gear, thereby reducing an engagement range between the inner tooth gear and the outer tooth gear to obtain excellent durability and reduce power loss.
According to an embodiment of the disclosure, there is provided a method for designing a tooth profile of a cycloidal gear of a gear shift actuator in which an outer tooth gear is provided inside the inner tooth gear, and the inner tooth gear and the outer tooth gear are engaged with each other and rotated, in which a design pitch circle radius (Ri1) of the outer tooth gear is obtained by subtracting a predetermined backlash (x) from a theoretical pitch circle radius (Ri) of the outer tooth gear, and a design rolling circle radius (ri1) of the outer tooth gear is obtained using the design pitch circle radius (Ri1) of the outer tooth gear.
In addition, the design rolling circle radius (ri1) of the outer tooth gear may be smaller than the theoretical rolling circle radius (ri) of the outer tooth gear.
In addition, the inner tooth gear may be designed with a theoretical pitch circle radius (Ro) and a theoretical rolling circle radius (ro).
In addition, an eccentric amount of the outer tooth gear may be designed to be equal to the theoretical eccentric amount (e).
In addition, a design clearance amount (T1), which is a distance between an outer diameter of a rolling circle of the inner tooth gear and an outer diameter of a rolling circle of the outer tooth gear, may be greater than a theoretical clearance amount (T).
According to another embodiment of the disclosure, there is provided a method for designing a tooth profile of a cycloidal gear of a gear shift actuator in which an outer tooth gear is provided inside the inner tooth gear, and the inner tooth gear and the outer tooth gear are engaged with each other and rotated, in which a design pitch circle radius (Ro1) of the inner tooth gear is obtained by adding a predetermined backlash (x) to a theoretical pitch circle radius (Ro) of the inner tooth gear, and a design rolling circle radius (ro1) of the inner tooth gear is obtained using a design pitch circle radius (Ro1) of the inner tooth gear.
In addition, the design rolling circle radius (ro1) of the inner tooth gear may be greater than the theoretical rolling circle radius (ro) of the inner tooth gear.
In addition, the outer tooth gear may be designed with a theoretical pitch circle radius (Ri) and a theoretical rolling circle radius (ri).
In addition, an eccentric amount of the outer tooth gear may be designed to be equal to the theoretical eccentric amount (e).
In addition, a design clearance amount (T1), which is a distance between an outer diameter of a rolling circle of the inner tooth gear and an outer diameter of a rolling circle of the outer tooth gear, may be greater than the theoretical clearance amount (T).
According to another embodiment of the disclosure, there is provided a cycloidal gear of a gear shift actuator manufactured by the method for designing a tooth profile of a cycloidal gear of a gear shift actuator and formed so that there is a predetermined backlash between the inner tooth gear and the outer tooth gear.
According to another embodiment of the disclosure, there is provided a gear shift actuator including the cycloidal gear of the gear shift actuator, including an input shaft coupled to any one of the inner tooth gear and outer tooth gear and an output shaft coupled to the other.
The method for designing a tooth profile of a cycloidal gear of a gear shift actuator of the disclosure has the advantage of enabling smooth engagement between the inner tooth gear and the outer tooth gear, reducing the engagement range of the inner tooth gear and the outer tooth gear, and obtaining excellent durability and reducing power loss.
In addition, since a backlash is provided by changing a radius of a rolling circle of the inner tooth gear or outer tooth gear of the cycloidal gear, a shape of the gear may be machined using the general cycloidal gear machining method, thereby facilitating manufacture and improving machining precision.
Hereinafter, a method for designing a tooth profile of a cycloidal gear of a gear shift actuator according to the disclosure having the configuration described above will be described in detail with reference to the accompanying drawings.
First, referring to
Theoretical pitch circle radius of inner tooth gear (Ro)={cycloid module (M)×number of teeth of inner tooth gear (No)}/2 <Formula 1>
Theoretical rolling circle radius of inner tooth gear (ro)={theoretical pitch circle radius of inner tooth gear (Ro)/number of teeth of inner tooth gear (No)}/2 <Formula 2>
Theoretical pitch circle radius of outer tooth gear (Ri)={cycloid module (M)×number of teeth of outer tooth gear (Ni)}/2 <Formula 3>
Theoretical rolling circle radius of outer tooth gear (ri)={Theoretical pitch circle radius of outer tooth gear (Ri)/number of teeth of outer tooth gear (Ni)}/2 <Formula 4>
As described above, a cycloidal gear designed by applying the basic formula (theoretical formula) of the cycloidal gear of the gear shift actuator of the related art includes an outer tooth gear 20 inside the inner tooth gear 10, and it is designed so that the center of the outer tooth gear 20 is eccentric by a theoretical eccentric amount (e) to one side from the center of the inner tooth gear 10. In addition, on the side in which a distance between the inner tooth gear 10 and the outer tooth gear 20 is close, the teeth of the gears may be engaged with each other and rotated by a specific angular range (a gear engagement range) in a state in which the teeth of the gears are spaced apart from each other with a specific theoretical clearance amount T, and on the side in which a distance between the inner tooth gear 10 and the outer tooth gear 20 is far, the teeth of the gears are spaced apart from each other with a specific theoretical clearance amount T and may not be engaged with each other.
Referring to
Design pitch circle radius of outer tooth gear (Ri1)={cycloid module (M)×number of teeth of outer tooth gear (Ni)}/2−backlash (x) <Formula 5>
Design rolling circle radius of outer tooth gear (ri1)={design pitch circle radius of outer tooth gear (Ri1)/number of teeth of outer tooth gear (Ni)}/2 <Formula 6>
Here, in the method for designing a tooth profile of a cycloidal gear of a gear shift actuator according to an embodiment of the disclosure, an inner tooth gear 100 may be designed with a theoretical pitch circle radius Ro and a theoretical rolling circle radius ro, and a theoretical eccentric amount el of an outer tooth gear 200 may be designed to be equal to the theoretical eccentric amount e.
Therefore, as described above, the cycloidal gear designed by applying the method for designing a tooth profile of a cycloidal gear of a gear shift actuator according to an embodiment of the disclosure may be designed such that the outer tooth gear 200 is provided inside the inner tooth gear 100 and the center of the outer tooth gear 200 is eccentric from the center the inner tooth gear 100 by the theoretical eccentric amount e to one side. In addition, on the side where a distance between the inner tooth gear 100 and the outer tooth gear 200 is close, the teeth of the gears are spaced apart from each other with a specific design clearance amount T1, so that the teeth may be engaged with each other by a specific angular range (a gear engagement range) to be rotated, and on the side where the distance between the inner tooth gear 100 and the outer tooth gear 200 is far, the teeth of the gears are spaced apart from each other with a specific design clearance amount T1 and may not be engaged with each other. At this time, as shown, it can be seen that the gear engagement range of the disclosure is significantly reduced, compared to the gear engagement range of the cycloidal gear designed by applying the basic formula.
Here, since the outer tooth gear 200 according to the disclosure is applied with a predetermined backlash value x, the design pitch circle radius Ri1 of the outer tooth gear is designed to be smaller than the theoretical pitch circle radius Ri of the outer tooth gear. Also, accordingly, the design rolling circle radius ri1 of the outer tooth gear is smaller than the theoretical rolling circle radius ri of the outer tooth gear. That is, in the disclosure, by forming the pitch circle radius of the outer tooth gear 200 to be smaller than the theoretical value by applying backlash, the design rolling circle radius ri1 of the outer tooth gear may be formed to be smaller than the theoretical value, so that an oil film may be maintained between tooth surfaces of the gears by the amount of backlash, thereby designing a cycloidal gear with excellent durability and high efficiency (reduced power loss). In addition, since the outer tooth gear is designed in the form of a theoretical cycloid curve rather than a form arbitrarily deformed from the cycloid curve form, the shape of the gear may be machined using the general cycloidal gear machining method, and therefore, manufacture may be facilitated and machining precision may be improved.
In addition, as shown, in the cycloidal gear designed by applying the method for designing a tooth profile of a cycloidal gear of a gear shift actuator according to an embodiment of the disclosure, since the design rolling circle radius ri1 of the outer tooth gear is formed to be smaller than the theoretical value, the design clearance amount T1, which is a distance between the outer diameter of the rolling circle of the inner tooth gear 100 and the outer diameter of the rolling circle of the outer tooth gear 200, may be formed to be greater than the theoretical clearance amount T. Accordingly, an oil film may be maintained in the gap between the tooth surfaces of the inner tooth gear 100 and the outer tooth gear 200, and a contact area between the tooth surfaces of the gears may be reduced, resulting in excellent durability and reduced power loss.
In addition, a formula for designing a tooth profile of a cycloidal gear of a gear shift actuator according to another embodiment of the disclosure is as follows.
Design pitch circle radius of inner tooth gear (Ro1)={cycloid module (M)×number of teeth of inner tooth gear (No)}/2+backlash (x) <Formula 7>
Design rolling circle radius of inner tooth gear (ro1)={design pitch circle radius of inner tooth gear (Ro1)/number of teeth of inner tooth gear (No)}/2 <Formula 8>
Here, in the method for designing a tooth profile of a cycloidal gear of a gear shift actuator according to another embodiment of the disclosure, the outer tooth gear 200 may be designed with a theoretical pitch circle radius Ri and a theoretical rolling circle radius ri, and the eccentric amount el of the outer tooth gear 200 may be designed to be equal to the theoretical eccentric amount e.
Therefore, as described above, the cycloidal gear designed by applying the method for designing a tooth profile of a cycloidal gear of a gear shift actuator according to an embodiment of the disclosure may be designed such that the outer tooth gear 200 is provided inside the inner tooth gear 100 and the center of the outer tooth gear 200 is eccentric from the center the inner tooth gear 100 by the theoretical eccentric amount e to one side. In addition, on the side where a distance between the inner tooth gear 100 and the outer tooth gear 200 is close, the teeth of the gears are spaced apart from each other with a specific design clearance amount T1, so that the teeth may be engaged with each other by a specific angular range (a gear engagement range) to be rotated, and on the side where the distance between the inner tooth gear 100 and the outer tooth gear 200 is far, the teeth of the gears are spaced apart from each other with a specific design clearance amount T1 and may not be engaged with each other. Also, in this case, as shown, it can be seen that the gear engagement range of the disclosure is significantly reduced, compared to the gear engagement range of the cycloidal gear designed by applying the basic formula.
Here, since the inner tooth gear 100 according to the disclosure is applied with a predetermined backlash value x, the design pitch circle radius Ro1 of the inner tooth gear is designed to be greater than the theoretical pitch circle radius Ro of the inner tooth gear. Also, accordingly, the design rolling circle radius ro1 of the inner tooth gear is greater than the theoretical rolling circle radius ro of the inner tooth gear. That is, in the disclosure, by forming the pitch circle radius of the inner tooth gear 100 to be greater than the theoretical value by applying backlash, the design rolling circle radius ro1 of the inner tooth gear may be formed to be greater than the theoretical value, so that an oil film may be maintained between tooth surfaces of the gears by the amount of backlash, thereby designing a cycloidal gear with excellent durability and high efficiency (reduced power loss). In addition, since the outer tooth gear is designed in the form of a theoretical cycloid curve rather than a form arbitrarily deformed from the cycloid curve form, the shape of the gear may be machined using the general cycloidal gear machining method, and therefore, manufacture may be facilitated and machining precision may be improved.
In addition, in the cycloidal gear designed by applying the method for designing a tooth profile of a cycloidal gear of a gear shift actuator according to another embodiment of the disclosure, since the design rolling circle radius ro1 of the inner tooth gear is formed to be greater than the theoretical value, the design clearance amount T1, which is a distance between the outer diameter of the rolling circle of the inner tooth gear 100 and the outer diameter of the rolling circle of the outer tooth gear 200, may be formed to be greater than the theoretical clearance amount T. Accordingly, an oil film may be maintained in the gap between the tooth surfaces of the inner tooth gear 100 and the outer tooth gear 200, and a contact area between the tooth surfaces of the gears may be reduced, resulting in excellent durability and reduced power loss.
In addition, the cycloidal gear of the gear shift actuator of the disclosure is designed and then manufactured by the method for designing a tooth profile of a cycloidal gear of a gear shift actuator as described above, so that a predetermined backlash may be formed between the inner tooth gear 100 and the outer tooth gear 200.
In addition, the gear shift actuator of the disclosure may include the aforementioned cycloidal gear and may include an input shaft coupled to either the inner tooth gear 100 or the outer tooth gear 200 and an output shaft coupled to the other.
The disclosure is not limited to the above embodiments, and the scope of application is diverse and a person skilled in the art to which the disclosure pertains may practice various modifications without departing from the gist of the disclosure claimed in the claims.
| Number | Date | Country | Kind |
|---|---|---|---|
| 10-2020-0159759 | Nov 2020 | KR | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/KR2021/017396 | 11/24/2021 | WO |
