CN214838236U - Driven gear for gear transmission - Google Patents
Driven gear for gear transmission Download PDFInfo
- Publication number
- CN214838236U CN214838236U CN202022862313.1U CN202022862313U CN214838236U CN 214838236 U CN214838236 U CN 214838236U CN 202022862313 U CN202022862313 U CN 202022862313U CN 214838236 U CN214838236 U CN 214838236U
- Authority
- CN
- China
- Prior art keywords
- gear
- driven gear
- output
- teeth
- eccentric
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Images
Abstract
The utility model discloses a be used for gear drive's driven gear belongs to the speed reducer field, any point satisfies certain formula on driven gear's the eccentric wheel profile curve, driven gear profile curve is got by this driven gear's eccentric wheel profile curve inward-fetching equidistance curve. The utility model has the advantages that: the driven gear designed by the formula is attached to the driving wheel for transmission, the limitation of the relation of tooth number and diameter can be avoided, the size of the driven gear can be kept not to be synchronously enlarged under the condition of realizing a large transmission ratio, and even the transmission ratio is finally unrelated to the size ratio of the gear, so that the purpose of high-power transmission is achieved.
Description
Technical Field
The utility model relates to a speed reducer field particularly, relates to a driven gear for gear drive.
Background
The mechanical technology of the machine has been developed for hundreds of years, various transmission modes are abundant, the gear transmission of pure machinery is more perfect, and the mature solutions can be found according to almost various mechanical design requirements, but the gear multi-stage transmission type reducer is rapidly developed in the last ten years and is predicted to be in the ubiquitous robot market in the future, the traditional gear multi-stage transmission type reducer is in a marginal position, and most market requirements are occupied by the high-price and expensive RV reducer and the harmonic reducer. The conventional structure of the gear requires that the minimum number of teeth of the gear must meet a certain value, so that the diameter of the teeth of the driven wheel is too large, and the speed reducer after multistage cascading is heavy or in a multistage cascading mode, so that the additional requirements that the structure of the robot needs to be small and light cannot be met.
SUMMERY OF THE UTILITY MODEL
To reach the multiple relation that higher drive ratio must accord with the diameter number of teeth, driven wheel number of teeth diameter is too big, multistage cascade speed reducer structure heavy scheduling problem that exist to prior art speed reducer gear drive structure, the utility model provides a cooperation for gear drive utilizes the gear between, does not receive the restriction of number of teeth diameter relation, can also keep self size can not synchronous grow under the condition of realizing big drive ratio, finally lets drive ratio and gear size ratio irrelevantly of own even, has reached high-power driven purpose. The specific technical scheme is as follows:
driven gear for gear transmission, wherein any point M (x) in eccentric profile curve of driven geart，yt) The following formula is satisfied:
the center of the driven gear is an original point, t is (0, 2N pi), N is the number of the teeth of the driven gear, N is an integer larger than 1, A is the axial distance between the driven gear and the driving wheel, and B is the eccentric distance of the driving wheel;
the profile curve of the driven gear is obtained by taking an equidistant curve with the distance being the radius of the driving wheel inwards from the profile curve of the eccentric gear of the driven gear.
Each driving wheel is attached to a curve corresponding to one tooth on the driven gear, and the outer circumferential surface of each driving wheel is in contact with different positions on the curve corresponding to the corresponding tooth and is in rolling connection with the corresponding tooth. In the process that the driving wheel is in contact with the corresponding gear of the driven gear, the driven gear rotates for 1/N of a circle when the driving wheel rotates for one circle, and then the driving wheel is attached to the curve corresponding to the next tooth on the driven gear and drives the driven gear to rotate, so that the aim of speed reduction transmission is fulfilled.
Preferably, the number of the driven gear teeth N is 2-21.
Preferably, the number N of the teeth of the driven gear is 4-8.
Preferably, the number of teeth N of the driven gear is 4.
Preferably, the number of teeth N of the driven gear is 5.
Preferably, the number of teeth N of the driven gear is 6.
Preferably, the number of teeth N of the driven gear is 8.
When the circumferential profile surface of the driving wheel is contacted with the concave center of each tooth of the driven gear, the friction force of the driving wheel on the driven gear is minimum, and when the circumferential profile surface of the driving wheel is contacted with the convex center of each tooth of the driven gear, the friction force of the driving wheel on the driven gear is maximum.
When the eccentricity B1 of the driving wheel is larger, the concave-convex effect of the circumferential surface profile of the driven gear is more obvious.
The utility model also provides a gear drive structure, including foretell driven gear.
Has the advantages that:
adopt the utility model discloses technical scheme produces beneficial effect as follows:
(1) each driving wheel is attached to a curve corresponding to one tooth on the driven gear, and the outer circumferential surface of each driving wheel is in contact with different positions on the curve corresponding to the corresponding tooth and is in rolling connection with the corresponding tooth. In the process that the driving wheel is in contact with the corresponding gear of the driven gear, the driven gear rotates for 1/N of a circle when the driving wheel rotates for one circle, and then the driving wheel is attached to the curve corresponding to the next tooth on the driven gear and drives the driven gear to rotate, so that the aim of speed reduction transmission is fulfilled.
(2) The structure of the driving wheel is greatly simplified, the structure of the driving wheel is an eccentric wheel, the processing precision and the strength cost can be well controlled, and the processing problem equal to half of the processing problem in a transmission structure is solved.
(3) The driven gear structure is similar to a polygonal structure with concave edges, is completely different from the existing gear tooth structure in shape, can be directly processed by wire cutting and slow-moving wires, is low in manufacturing cost, is matched with an eccentric driving wheel complete set structure with a simple structure, and can be manufactured under the condition of lower cost, so that the manufactured speed reducer has a proper economic value.
(4) The transmission between the driving wheel and the driven gear is rolling friction instead of sliding friction, and the transmission efficiency and precision are further improved and the damage to the driving wheel is reduced through rubbing transmission.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings that are required to be used in the embodiments will be briefly described below, it should be understood that the following drawings only illustrate some embodiments of the present invention, and therefore should not be considered as limiting the scope, and for those skilled in the art, other related drawings can be obtained according to the drawings without inventive efforts.
FIG. 1 is a schematic diagram of a gear transmission unit including a 2-tooth driven gear according to the present invention;
FIG. 2 is a schematic diagram of a gear transmission unit including a 3-tooth driven gear according to the present invention;
FIG. 3 is a schematic diagram of a gear transmission unit including 4-tooth driven gears according to the preferred embodiment of the present invention;
FIG. 4 is a schematic diagram of a gear transmission unit including a 5-tooth driven gear according to the present invention;
FIG. 5 is a schematic diagram of a gear transmission unit including a 6-tooth driven gear according to the present invention;
FIG. 6 is a schematic diagram of a gear transmission unit including a driven gear with 8 teeth according to the preferred embodiment of the present invention;
FIG. 7 is a schematic view of a gear transmission unit including a 10-tooth driven gear according to the present invention;
FIG. 8 is a schematic diagram of a gear transmission unit including a 14-tooth driven gear according to the present invention;
FIG. 9 is a schematic diagram of the eccentric profile of the preferred driven gear of the present invention;
FIG. 10 is a perspective view of a preferred gear transmission structure of the present invention;
FIG. 11 is a perspective view of a preferred gear transmission structure of the present invention;
FIG. 12 is a third perspective view of the preferred gear transmission structure of the present invention;
FIG. 13 is a schematic diagram of an eccentric profile curve of a preferred output gear of the present invention;
FIG. 14 is a schematic diagram of the eccentric profile of the preferred input gear of the present invention;
FIG. 15 is a schematic view of the preferred 2-fold transmission speed reduction structure of the present invention;
FIG. 16 is a schematic view of the preferred 3-fold transmission reduction structure of the present invention;
FIG. 17 is a schematic view of the preferred 4-fold transmission speed reduction structure of the present invention;
FIG. 18 is a schematic view of the preferred 5-fold transmission reduction structure of the present invention;
FIG. 19 is a schematic view of the preferred 6-fold transmission reduction structure of the present invention;
FIG. 20 is a schematic view of the preferred 8-fold transmission reduction structure of the present invention;
FIG. 21 is a schematic view of the preferred 10 times transmission reduction structure of the present invention;
FIG. 22 is a schematic view of the preferred 14 times transmission reduction structure of the present invention;
in the figure: 101. a driving wheel; 102. a driven gear; 103. driven gear eccentric profile curve;
104. a driven gear profile curve; 1. an input component; 11. inputting an eccentric wheel set; 12. an input gear set;
1011. inputting an eccentric wheel; 1021. an input gear; 1031. an input gear eccentric profile curve;
1041. inputting a gear profile curve; 111. inputting an eccentric wheel main body; 112. a rolling bearing; 2. an output component;
21. an output gear set; 22. an output eccentric wheel set; 201. an output gear; 202. an output eccentric wheel;
203. an output gear eccentric profile curve; 204. outputting a gear profile curve; 3. and (7) mounting a disc.
Detailed Description
To make the objects, technical solutions and advantages of the embodiments of the present invention clearer, the drawings of the embodiments of the present invention are combined to clearly and completely describe the technical solutions of the embodiments of the present invention, and obviously, the described embodiments are some embodiments of the present invention, not all embodiments. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative work belong to the protection scope of the present invention. Thus, the following detailed description of the embodiments of the present invention, presented in the accompanying drawings, is not intended to limit the scope of the invention, as claimed, but is merely representative of selected embodiments of the invention. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative work belong to the protection scope of the present invention.
As shown in FIG. 9, a driven gear 102 for gear transmission is provided, wherein any point M (x) in the eccentric contour curve 103 of the driven geart，yt) The following formula is satisfied:
the center of the driven gear 102 is an origin, t is (0, 2N pi), N is the number of teeth of the driven gear 102, N is an integer greater than 1, a is the axial distance between the driven gear 102 and the driving wheel 101, and B is the eccentric distance of the driving wheel 101;
the driven gear contour curve 104 is obtained by taking an equidistant curve with the radius R1 of the driving wheel 101 inwards from the driven gear eccentric contour curve 103.
Specifically, the driving wheel 101 is an eccentric wheel.
By adopting the driving wheel 101, the structure is greatly simplified, the structure is an eccentric wheel, the processing precision and the strength cost can be well controlled, and the processing problem equal to half of the processing problem in a transmission structure is solved.
In a preferred embodiment, the number N of the driven gear 102 teeth is 2-21.
In a preferred embodiment, the number of teeth N of the driven gear 102 is 4-8.
In a preferred embodiment, the number N of the driven gear 102 is 4.
In a preferred embodiment, the number N of the driven gear 102 is 5.
In a preferred embodiment, the number N of the driven gear 102 is 6.
In a preferred embodiment, the number N of the driven gear 102 is 8.
Each driving wheel 101 is attached to a curve corresponding to one tooth on the driven gear 102, and the outer circumferential surface of each driving wheel 101 is in contact with different positions on the curve of the corresponding tooth and is in rolling connection with the corresponding tooth. In the process of contacting the driving wheel 101 and the corresponding gear of the driven gear 102, the driven gear 102 rotates for 1/N of a circle every time the driving wheel 101 rotates for a circle, and then the driving wheel 101 is attached to the curve corresponding to the next tooth on the driven gear 102, so that the purpose of speed reduction transmission is achieved.
Specifically, as shown in fig. 1 to 8, when the number of the teeth of the driven gear 102 is 2, 3, 4, 5, 6, 8, 10, 14, each driven gear 102 rotates 1/N of a revolution for each revolution of the driving wheel 101, and therefore, when the number of the teeth of the driven gear 102 is 2, 3, 4, 5, 6, 8, 10, 14, the driving wheel 101 rotates one revolution, and the driven gear 102 rotates 1/2, 1/3, 1/4, 1/5, 1/6, 1/8, 1/10, or 1/14 revolutions, so as to achieve the purpose of speed reduction.
When the circumferential contour surface of the driving wheel 101 contacts the concave center of each tooth of the driven gear 102, the friction force of the driving wheel 101 received by the driven gear 102 is the smallest, and when the circumferential contour surface of the driving wheel 101 contacts the convex center of each tooth of the driven gear 102, the friction force of the driving wheel 101 received by the driven gear 102 is the largest.
When the eccentricity B1 of the drive pulley 101 is larger, the concave-convex effect of the circumferential surface profile of the driven gear 102 is more remarkable.
In the implementation operation process, in order to ensure the uniformity of the action of the force of the driving wheel 101 on the driven gear 102, when the circumferential profile surface of a certain driving wheel 101 is positioned at the concave center position of the teeth on the driven gear 102, if the number of the teeth of the driven gear 102 is odd, the circumferential profile surface of the driving wheel 101 opposite to the driven gear is contacted with the convex center of the teeth on the driven gear 102; if the number of teeth of the driven gear 102 is even, two driving wheels 101 are arranged on the left side and the right side of the opposite face of the driven gear and are arranged in a triangular shape, so that the problem of insufficient friction force at the position can be solved.
In the implementation operation process, the number of the driving wheels 101 and the number of the teeth of the driven gear have a certain correlation, half or equal to the number of the teeth of the driven gear 102, preferably half of the number of the teeth of the driven gear 102, for example, when the number of the teeth of the driven gear 102 is 8, the number of the driving wheels 101 is preferably 4; if the number of the driven gears 102 is 6, the number of the driving gears 101 may be 3 or 6.
The utility model discloses specific still design a gear drive structure, including foretell driven gear 102.
As shown in fig. 10 to 12, the gear transmission structure includes an input assembly 1 and an output assembly 2, and the output assembly 2 includes an output gear 201 and more than two output eccentrics 202 uniformly distributed in the circumferential direction of the output gear 201 and attached to the output gear 201. The output eccentric wheel 202 is attached to the output gear 201 to drive the output gear 201 to move, so that the purpose of gear reduction transmission is achieved.
Each output eccentric wheel 202 is attached to a curve corresponding to one tooth on the output gear 201, and the outer circumferential surface of the output eccentric wheel 202 is in contact with different positions on the curve of the corresponding tooth and is in rolling connection. In the process that the output eccentric wheel 202 is in contact with the corresponding gear of the output gear 201, every time the output eccentric wheel 202 rotates for one circle, the output gear 201 rotates for 1/N1 circles, and then the output eccentric wheel 202 is fitted with the curve corresponding to the next tooth on the output gear 201 and drives the output gear to rotate, so that the purpose of speed reduction transmission is achieved.
As shown in FIG. 13, any point M (x) in the output gear eccentric profile curve 203t，yt) The following formula is satisfied:
where the center of the output gear 201 is the origin, and t is (0, 2N)1π]N1 is the number of teeth of the output gear 201, N1 is an integer greater than 1, a is the axial distance of two wheels, and B1 is the eccentricity of the output eccentric 202.
In a preferred embodiment, output gear profile curve 204 is obtained by equidistant curves of output gear eccentric profile curve 203 inwardly spaced by a radius R1 of output eccentric 202.
The output gear contour curve 204 obtained by adopting the formula can ensure that the outer circumferential surface of the output gear and the output eccentric wheel 202 are always in a fit state, and the output eccentric wheel 202 and the output gear 201 are in rubbing transmission.
As a preferred embodiment, the number of the output eccentrics 202 distributed in the circumferential direction of the output gear 201 can be controlled as required, and the occupied space of the output eccentrics 202 on the outer circumferential surface of the output gear 201, the transmission stability, the transmission efficiency and the like are taken into comprehensive consideration, and several preferred schemes are adopted here.
N1 output eccentric wheels 202 can be uniformly distributed on the circumference of the output gear 201; the number of teeth N1 of the output gear 201 may be 3-21 teeth. The number of teeth N1 of the output gear 201 may be 4-8 teeth.
In the process of operation, it is found that the transmission efficiency is relatively good when the number of teeth N1 of the output gear 201 is 8.
When the circumferential contour surface of the output eccentric 202 is in contact with the concave center of each tooth of the output gear 201, the output gear 201 receives the smallest frictional force of the output eccentric 202, and when the circumferential contour surface of the output eccentric 202 is in contact with the convex center of each tooth of the output gear 201, the output gear 201 receives the largest frictional force of the output eccentric.
It is easily understood that the concave-convex effect of the circumferential surface profile of the output gear 201 is more pronounced as the eccentricity B1 of the output eccentric 202 is larger.
In order to ensure the uniformity of the force applied by the output gear 201 to the output eccentric 202 during the operation, when the peripheral contour surface of one output eccentric 202 is at the concave center position of the teeth on the output gear 201, if the number of the teeth of the output gear 201 is odd, the peripheral contour surface of the output eccentric 202 opposite to the peripheral contour surface is contacted with the convex center of the teeth on the output gear 201; if the number of teeth of the output gear 201 is even, two output eccentric wheels 202 are arranged on the opposite left side and the opposite right side of the output gear in a triangular arrangement to solve the problem of insufficient friction force at the positions.
In the implementation operation process, the number of the output eccentrics 202 has a certain correlation with the number of teeth of the output gear 201, half or equal to the number of teeth of the output gear 201, preferably half of the number of teeth of the output gear 201, for example, when the number of teeth of the output gear 201 is 8, the number of the output eccentrics 202 is preferably 4; if the number of teeth of the output gear 201 is 6, the number of the output eccentric wheels 202 may be 3 or 6.
As a preferred embodiment, as shown in fig. 10 to 12, the transmission structure further includes a mounting plate 3, and the input module 1 and the output module 2 are respectively mounted on two side surfaces of the mounting plate 3.
As a preferred embodiment, the output assembly 2 includes an output gear set 21 formed by overlapping W1 output gears 201 with a central shaft, and more than two sets of output eccentric wheel sets 22 uniformly distributed in the circumferential direction of the output gear set 21, each set of output eccentric wheel sets 22 is formed by rigidly and coaxially connecting W1 output eccentric wheels 202, and W1 is an integer greater than or equal to 2;
each layer of the output eccentric wheels 202 in the output eccentric wheel set 22 are uniformly distributed in the outer circumferential direction of the output gear 201 of the corresponding layer in the output gear set 21 and are attached to the outer circumferential profile of the output gear 201 of the corresponding layer.
In a preferred embodiment, the number of output gears 201 in the output gear set 21, W1, is 3-6.
In the test process, when the number W1 of the output gears 201 in the output gear set 21 is 4, the transmission stability is better.
The output gear set 21 formed by overlapping a plurality of output gears 201 is adopted for transmission, the contact parts of the concave-convex edges on the output gears 201 on different layers in the same output gear set 21 and the corresponding output eccentric wheels 202 are different, the transmission stability between the output eccentric wheel set 22 and the output gear set 21 is greatly improved, and therefore stable and smooth transmission of the output eccentric wheel set 22 to the output gear set 21 is realized.
In a preferred embodiment, the output gear set 21 is located at a position in the circumferential direction of the output gear 201 located at the lower position from top to bottom such that the output gear 201 located at the upper position rotates clockwise around the central axis
And obtaining the compound.
In a preferred embodiment, the output gear set 21 is located at a position in the circumferential direction of the output gear 201 located at a lower position from top to bottom such that the output gear 201 located at an upper position rotates counterclockwise around a central axis
And obtaining the compound.
As a preferred embodiment, as shown in fig. 10, the input assembly 1 includes an input eccentric 1011 and input gears 1021 uniformly distributed in the circumferential direction of the input eccentric 1011 and conforming to the outer circumferential profile of the input eccentric 1011, and each of the input gears 1021 has a central shaft rigidly and coaxially connected to a central shaft of one of the output eccentrics 202. The input eccentric wheel 1011 divergently drives the input gear 1021 to form a stable single-stage driving structure, then the input gear 1021 is gathered again through the output eccentric wheel 202 and drives back inwards to drive the output gear 201 to rotate, a complete two-stage transmission driving structure is formed, and the whole transmission process of the speed reducer with a large transmission ratio is completed through two transmissions.
As shown in fig. 14, any point M in the eccentric profile 1031 of the input gear2(xt，yt) The following formula is satisfied:
where the center of the input gear 1021 is the origin, and t is (0, 2N)2π]N2 represents the number of teeth of the input gear 1021, N2 represents an integer greater than 1, a represents the axial distance between two wheels, and B2 represents the eccentricity of the input eccentric 1011.
In a preferred embodiment, the input gear profile curve 1041 is obtained by taking an equidistant curve of the input gear eccentric profile curve 1031 to a distance of the radius R3 of the input eccentric 1011.
In a preferred embodiment, the number of teeth N2 of the input gear 1021 is equal to the number of teeth of the output gear 201.
As a preferred embodiment, the input assembly 1 includes an input eccentric wheel set 11 formed by overlapping W2 input eccentric wheels 1011 with a central shaft, and two or more input gear sets 12 uniformly distributed in the circumferential direction of the input eccentric wheel set 11, each input gear set 12 is formed by coaxially connecting W2 input eccentric wheel sets 11, and W2 is an integer greater than or equal to 2;
each layer of the input gears 1021 in the input gear set 12 is uniformly distributed in the direction of the outer circumference of the input eccentric wheel 1011 on the corresponding layer in the input eccentric wheel set 11 and is fitted with the outer circumference of the input eccentric wheel 1011 on the corresponding layer.
In a preferred embodiment, the input gear set 12 is arranged at a position in a circumferential direction of the input gear 1021 at a lower position from top to bottom such that the input gear 1021 at the upper position rotates clockwise around a central axis
And obtaining the compound.
In a preferred embodiment, the input gear set 12 is located at a position circumferentially below the input gear 1021 from top to bottom such that the input gear located above rotates counterclockwise about a central axis
And obtaining the compound.
In a preferred embodiment, each of the input eccentrics 1011 of the input eccentric wheel set 11 is composed of an input eccentric wheel main body 111 and a rolling bearing 112 fitted around the input eccentric wheel main body 111, and the outer diameter of the rolling bearing 112 is equal to the diameter of the input eccentric wheel 1011.
The diameter of the driving gear and the diameter of the driven gear of the speed reducer obtained by adopting the gear transmission structure can be approximately the same, when one driving wheel transmits N times of gears, the periphery of the driving gear can simultaneously drive a plurality of N times of gears in a surrounding manner, and the problem that when the traditional single-stage transmission gear is used for gear transmission with a gear ratio, a single gear cannot simultaneously drive a plurality of large gears on the same plane due to insufficient space around the driving gear is solved.
As shown in fig. 15-22, the input assembly 1 has 2, 3, 4, 5, 6, 8, 10, 14 input gears 1021, the input eccentric 1011 fits a curve corresponding to one tooth on each input gear 1021, and the outer circumferential surface of the input eccentric 1011 contacts and is in rolling connection with different positions on the curve corresponding to the corresponding tooth. In the process of gear contact between the input eccentric wheel 1011 and the input gear 1021, each input gear 1021 rotates for 1/N2 cycle every time the input eccentric wheel 1011 rotates for one cycle, so that when the number of teeth of the input gear 1021 is 2, 3, 4, 5, 6, 8, 10, 14, the input eccentric wheel 1011 rotates for one cycle, and the input gear 1021 rotates for 1/2, 1/3, 1/4, 1/5, 1/6, 1/8, 1/10, or 1/14 cycle, thereby achieving the purpose of speed reduction transmission.
When the application, input eccentric wheel 1011 in the control input subassembly 1 is rotatory, input eccentric wheel 1011 diverges drive input gear 1021, form firm single-stage drive structure, make drive gear rotational speed become 1/N2 of input eccentric wheel 1011 rotational speed, then output eccentric wheel 202 gathers again through input gear 1021 and drives inwards back, drive output gear 201 is rotatory, form complete two-stage transmission drive structure, the rotational speed of output gear 201 is 1/(N1N 2) of input eccentric wheel 1011 rotational speed this moment, the whole transmission process of speed reducer of big drive ratio has just been accomplished in twice transmission, drive the requirement according to the drive ratio around the input eccentric wheel 1011, can also with secondary gear drive in the utility model becomes tertiary or level four etc., the space that the drive structure occupy has been saved greatly.
The diameter of the driving gear and the driven gear of the speed reducer obtained by adopting the gear transmission structure can be approximately the same, and when one driving wheel transmits N times of gears, the periphery of the driving wheel can simultaneously drive a plurality of N times of gears in a surrounding manner, so that the problem that when the traditional single-stage transmission gear with a gear ratio is transmitted, a single gear cannot simultaneously drive a plurality of large gears on the same plane due to insufficient space around the driving gear is solved; and when the diameter sizes of the driving gear and the driven gear are approximately the same, the purpose of outputting in different transmission ratios can be realized.
In practical application, the kneading mode is different according to the length relationship between the circumference of the driving eccentric wheel and a section of profile curve corresponding to the driven gear. When the circumference of the driving eccentric wheel is equal to the length between a section of profile curve corresponding to the driven gear, each point of contact is just in a rolling static friction state; when the circumference of the driving eccentric wheel is larger than the length of a section of contour curve corresponding to the driven gear, namely the length of the driving eccentric wheel which rotates for one circle is larger than the length of one section of contour curve of the driven gear, the driven gear is suitable to be driven; when the circumference of the driving eccentric wheel is smaller than the length of a section of contour curve corresponding to the driven gear, namely the length of the driving eccentric wheel which rotates for one circle is smaller than the length of one section of contour curve of the driven gear, the driven gear can also be used as a driving wheel to drive the driving eccentric wheel to rotate, namely the driving eccentric wheel can be driven from the output end to the input end, and the purpose of acceleration is achieved.
The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (8)
1. A driven gear for a gear transmission, characterized in that any point M (x) in the eccentric profile curve of said driven geart，yt) The following formula is satisfied:
the center of the driven gear is an original point, t is (0, 2N pi), N is the number of the teeth of the driven gear, N is an integer larger than 1, A is the axial distance between the driven gear and the driving wheel, and B is the eccentric distance of the driving wheel;
the profile curve of the driven gear is obtained by taking an equidistant curve with the distance being the radius of the driving wheel inwards from the profile curve of the eccentric gear of the driven gear.
2. A driven gear for a gear transmission according to claim 1, wherein the number of teeth N of the driven gear is 2-21.
3. A driven gear for a gear transmission according to claim 2, wherein the number of teeth N of the driven gear is 4-8 teeth.
4. A driven gear for a gear transmission according to claim 3, wherein the number of teeth N of the driven gear is 4.
5. A driven gear for a gear transmission according to claim 3, wherein the number of teeth N of the driven gear is 5 teeth.
6. A driven gear for a gear transmission according to claim 3, wherein the number N of teeth of the driven gear is 6 teeth.
7. A driven gear for a gear transmission according to claim 3, wherein the number of teeth N of the driven gear is 8.
8. A gear transmission comprising a driven gear according to any one of claims 1 to 7.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202022862313.1U CN214838236U (en) | 2020-12-03 | 2020-12-03 | Driven gear for gear transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202022862313.1U CN214838236U (en) | 2020-12-03 | 2020-12-03 | Driven gear for gear transmission |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN214838236U true CN214838236U (en) | 2021-11-23 |
Family
ID=78802095
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202022862313.1U Active CN214838236U (en) | 2020-12-03 | 2020-12-03 | Driven gear for gear transmission |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN214838236U (en) |
-
2020
- 2020-12-03 CN CN202022862313.1U patent/CN214838236U/en active Active
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN214838236U (en) | Driven gear for gear transmission | |
| CN214838173U (en) | Multilayer gear transmission part | |
| CN214788895U (en) | Gear transmission unit | |
| CN215171909U (en) | Gear input transmission mechanism | |
| CN214788843U (en) | Gear output transmission mechanism | |
| CN109780163B (en) | Reciprocating type cylindrical sine end face oscillating tooth speed reducer | |
| CN214788844U (en) | Gear transmission structure | |
| CN112377574B (en) | Gear transmission structure | |
| CN214788842U (en) | Gear accelerating transmission structure | |
| CN215171908U (en) | Multilayer gear transmission mechanism | |
| CN112377572B (en) | Multistage gear drive structure | |
| CN214838174U (en) | Simple gear transmission structure | |
| CN208252678U (en) | Internal tooth flexbile gear speed reducer | |
| CN112377577A (en) | Gear input transmission mechanism | |
| CN214838175U (en) | Multistage gear drive structure | |
| CN112728010A (en) | Gear output transmission mechanism | |
| CN112377596A (en) | Gear transmission unit | |
| CN216279217U (en) | Speed reducing mechanism | |
| CN108468760A (en) | Internal tooth flexbile gear speed reducer | |
| CN112555356A (en) | Gear acceleration transmission unit | |
| CN112377575A (en) | Multilayer gear transmission mechanism | |
| CN112377573A (en) | Simple gear transmission structure | |
| CN112377576A (en) | Gear accelerating transmission structure | |
| CN2179489Y (en) | Compound stroke driving wave teeth speed reducer | |
| CN111946796A (en) | Multistage gear drive's harmonic speed reducer ware and robot |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant |