CN214788895U

CN214788895U - Gear transmission unit

Info

Publication number: CN214788895U
Application number: CN202022862323.5U
Authority: CN
Inventors: 贾天玖; 程议
Original assignee: Fujian Sipu Measurement Technology Co ltd
Current assignee: Fujian Sipu Measurement Technology Co ltd
Priority date: 2020-12-03
Filing date: 2020-12-03
Publication date: 2021-11-19
Anticipated expiration: 2030-12-03

Abstract

The utility model discloses a gear drive unit belongs to the speed reducer field, including an initiative eccentric wheel and a driven gear, initiative eccentric wheel outer circumferential surface with the laminating of driven gear's outer circumferential surface, just the number of teeth more than or equal to 2 of driven gear. The utility model has the advantages that: the cooperation between the driving eccentric wheel and the driven gear is utilized, the limitation of the relation of the diameters of the teeth is avoided, the self size can be kept not to be synchronously enlarged under the condition of realizing 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

Gear transmission unit

Technical Field

The utility model relates to a speed reducer field particularly, relates to a gear drive unit.

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, the heavy scheduling problem of multistage cascade speed reducer structure that exist to prior art speed reducer gear drive structure, the utility model provides a gear drive unit utilizes the cooperation between initiative eccentric wheel and the driven gear, does not receive the restriction of number of teeth diameter relation, can also keep self size can not synchronous grow under the condition that realizes big drive ratio, finally lets drive ratio and gear size ratio irrelevant itself even, has reached the driven purpose of high power. The specific technical scheme is as follows:

a gear transmission unit comprises a driving eccentric wheel and a driven gear, wherein any point M (x) in an eccentric profile curve of the driven gear_t，y_t) 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 eccentric wheel, and B is the eccentric distance of the driving eccentric wheel.

Preferably, the profile curve of the driven gear is obtained by taking an equidistant curve with the radius of the driving eccentric wheel from the inner side of the profile curve of the driven gear.

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.

Each driving eccentric wheel is attached to a curve corresponding to one tooth on the driven gear, and the outer circumferential surface of each driving eccentric wheel is in contact with different positions on the curve of the corresponding tooth and is in rolling connection. In the process that the driving eccentric wheel is in contact with the corresponding gear of the driven gear, the driven gear rotates for 1/N circle every time the driving eccentric wheel rotates for one circle, and then the driving eccentric 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.

When the peripheral contour surface of the driving eccentric wheel is contacted with the concave center of each tooth of the driven gear, the friction force of the driving eccentric wheel on the driven gear is minimum, and when the peripheral contour surface of the driving eccentric wheel is contacted with the convex center of each tooth of the driven gear, the friction force of the driving eccentric wheel on the driven gear is maximum.

When the eccentricity B of the driving eccentric wheel is larger, the concave-convex effect of the peripheral surface profile of the driven gear is more obvious.

The utility model also provides a gear drive structure, including above-mentioned gear drive unit.

Has the advantages that:

adopt the utility model discloses technical scheme produces beneficial effect as follows:

(1) each driving eccentric wheel is attached to a curve corresponding to one tooth on the driven gear, and the outer circumferential surface of each driving eccentric wheel 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 eccentric wheel with the corresponding gear of the driven gear, the driven gear rotates for 1/N circle when the driving eccentric wheel rotates for one circle, then the driving eccentric wheel is attached to the curve corresponding to the next tooth on the driven gear and continuously drives the driven gear to rotate, and the purpose of speed reduction transmission is achieved.

(2) The structure of the driving eccentric wheel is greatly simplified, the structure of the driving eccentric 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 speed reducer obtained by the gear transmission unit has the advantages that the transmission between the driving gear and the driven gear is not limited by the relation of the diameters of the teeth, the size of the speed reducer can be kept not to be synchronously enlarged under the condition of realizing a large transmission ratio, the transmission ratio is not related to the size ratio of the gear, the purpose of high-power transmission is achieved, the utilization space of the speed reducer is saved, and the manufactured speed reducer is lighter.

(4) The structure of driven gear is similar to the polygon structure with concave edge, and is completely different from the structural shape of the existing gear teeth, and the wire-electrode cutting slow-walking wire can be used for direct processing, so that the manufacturing cost is low, and the eccentric driving wheel complete structure with simple structure is matched, so that the manufactured speed reducer has proper economic value under the condition of lower cost.

(5) The transmission between the driving eccentric 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;

FIG. 23 is a schematic view of a preferred embodiment of the present invention including 2 input gears;

FIG. 24 is a schematic view of a preferred embodiment of the present invention including 3 input gears;

FIG. 25 is a schematic view of a preferred embodiment of the present invention including 4 input gears;

FIG. 26 is a schematic view of a preferred embodiment of the present invention including 5 input gears;

FIG. 27 is a schematic view of a preferred embodiment of the present invention including 6 input gears;

FIG. 28 is a schematic view of the preferred input assembly of the present invention including 7 input gears;

FIG. 29 is a schematic view of a preferred embodiment of the present invention including 8 input gears;

FIG. 30 is a schematic view of a preferred input assembly of the present invention including 9 input gears;

fig. 31 is a schematic diagram of an input assembly including 10 input gears according to the preferred embodiment of the present invention.

In the figure: 101. a driving eccentric 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. 1-9, the gear transmission unit comprises a driving eccentric 101 and a driven gear 102, said driven gear having any point M (x) in the eccentric profile curve 103_t，y_t) The following formula is satisfied:

the center of the driven gear 102 is an origin, t ═ 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 eccentric wheel 101, and B is the eccentric distance of the driving eccentric wheel 101.

In a preferred embodiment, the driven gear profile curve 104 is obtained by taking an equidistant curve of the driven gear eccentric profile curve 103 inwardly from the driving eccentric radius R1.

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.

Referring to fig. 1-8, the driving relationship between the driven gear 102 and the driving eccentric 101 is shown in the schematic diagrams when the number of the driven gear 102 is 2, 3, 4, 5, 6, 8, 10, 14.

In practice, it has been found that when the number of teeth N of the driven gear 102 is 8, the transmission efficiency is good.

Each driving eccentric wheel 101 is attached to a curve corresponding to one tooth on the driven gear 102, and the outer circumferential surface of each driving eccentric wheel 101 is in contact with different positions on the curve of the corresponding tooth and is in rolling connection. In the process that the driving eccentric wheel 101 is in contact with the corresponding gear of the driven gear 102, the driven gear 102 rotates for 1/N of a circle every time the driving eccentric wheel 101 rotates for one circle, and then the driving eccentric wheel 101 is fitted with the curve corresponding to the next tooth on the driven gear 102 and drives the next tooth to rotate, so that the purpose of speed reduction transmission is achieved.

Specifically, when the number of teeth of the driven gear 102 is 2, 3, 4, 5, 6, 8, 10, 14, respectively, each driven gear 102 rotates 1/N of a revolution per revolution of the driving eccentric 101, see fig. 1-8, so that when the number of teeth of the driven gear 102 is 2, 3, 4, 5, 6, 8, 10, 14, the driving eccentric 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.

The driven gear 102 receives the smallest frictional force of the driving eccentric 101 when the circumferential profile surface of the driving eccentric 101 is in contact with the concave center of each tooth of the driven gear 102, and the driven gear 102 receives the largest frictional force of the driving eccentric 101 when the circumferential profile surface of the driving eccentric 101 is in contact with the convex center of each tooth of the driven gear 102.

The concave-convex effect of the circumferential surface profile of the driven gear 102 becomes more remarkable as the eccentricity B1 of the driving eccentric 101 becomes larger.

The embodiment also provides a gear transmission structure, which comprises more than one group of gear transmission units.

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.

As shown in FIG. 13, any point M (x) in the output gear eccentric profile curve 203_t，y_t) 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.

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 attached to the curve corresponding to the next tooth on the output gear 201, so that the purpose of speed reduction transmission is achieved.

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 can be 3-21, and preferably, the number of teeth N1 of the output gear 201 can be 4-8.

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.

A plurality of output gears are overlapped to form an output gear set, and a plurality of output eccentric wheels are overlapped to form an output eccentric wheel set, so that the purpose is to improve the transmission stability. 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 to 12, 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(x_t，y_t) 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 profile curve of the driven gear is obtained by drawing the profile curve of the driven gear inward by an equidistant curve having a radius R3 of the driving eccentric.

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 gearset 12 is configured to be driven from aboveThe input gear 1021 at the lower position rotates counterclockwise around the 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.

As shown in fig. 23-31, the diameter of the driving gear and the driven gear of the speed reducer obtained by the gear transmission structure can be approximately the same, and when one transmission wheel transmits N times of gears, a plurality of N times of gears can be simultaneously driven around the transmission wheel, so that the problem that when the traditional single-stage transmission gear with a large 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.

As shown in fig. 15-22, the input assembly 1 has 2, 3, 4, 5, 6, 8, 10, and 14 input gears 1021, the input eccentric 1011 fits a curve corresponding to a 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 of 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 input gear 1021 gathers again through output eccentric wheel 202 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.

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

1. A gear transmission unit is characterized by comprising a driving eccentric wheel and a driven gear, wherein the outer circumferential surface of the driving eccentric wheel is attached to the outer circumferential surface of the driven gear, and the number of teeth of the driven gear is more than or equal to 2.

2. A gear transmission unit according to claim 1, wherein the number N of passive gear teeth is 2-21 teeth.

3. A gear transmission unit according to claim 2, characterised in that the number N of teeth of the driven gear is 4-8 teeth.

4. A gear transmission unit according to claim 3, characterised in that the number N of teeth of the driven gear is 4.

5. A gear transmission unit according to claim 4, characterised in that the number N of teeth of the driven gear is 5 teeth.

6. A gear transmission unit according to claim 5, characterised in that the number N of teeth of the driven gear is 6 teeth.

7. A gear transmission unit according to claim 6, characterised in that the number N of teeth of the driven gear is 8.

8. A gear transmission unit according to claim 2, characterised in that any point M (x) in the eccentric profile curve of the driven gear_t，y_t) The following formula is satisfied:

9. A gear transmission unit according to claim 8, wherein the driven gear profile curve is obtained by an equidistant curve inward of the driven gear profile curve by the radius of the driving eccentric.

10. A gear transmission arrangement, characterized by comprising a gear transmission unit according to any one of claims 1-9.