CN112377576A - Gear accelerating transmission structure - Google Patents

Gear accelerating transmission structure Download PDF

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Publication number
CN112377576A
CN112377576A CN202011397196.4A CN202011397196A CN112377576A CN 112377576 A CN112377576 A CN 112377576A CN 202011397196 A CN202011397196 A CN 202011397196A CN 112377576 A CN112377576 A CN 112377576A
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China
Prior art keywords
output
gear
input
eccentric wheel
eccentric
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陈晔
程议
贾天玖
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Fujian Sipu Measurement Technology Co ltd
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Fujian Sipu Measurement Technology Co ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/20—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members
    • F16H1/22—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/08—Profiling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/17—Toothed wheels

Abstract

The invention discloses a gear acceleration transmission structure, which belongs to the field of speed reducers and comprises an input assembly and an output assembly, wherein the output assembly comprises an output eccentric wheel and more than one output gear which is arranged on the circumferential surface of the output eccentric wheel and is attached to the output eccentric wheel, and the output eccentric wheel is an eccentric wheel. The invention has the beneficial effects that: the cooperation of more than two groups of gears is utilized, the gear transmission mechanism is not limited by the relation of tooth number and diameter, the self size can be kept from being enlarged synchronously under the condition of realizing large transmission ratio, and even the transmission ratio is finally unrelated to the size ratio of the gears, so that the purpose of high-power transmission is achieved.

Description

Gear accelerating transmission structure
Technical Field
The invention relates to the field of speed reducers, in particular to a gear acceleration transmission structure.
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 transmission of the pure machinery is rapidly developed in the last ten years and is predicted to be in the ubiquitous robot market in the future, the speed reducer manufactured by the traditional gear is gradually in the marginal position, the speed reducer manufactured by the traditional gear is gradually eliminated, the main reason is also caused by the characteristics of the gear, and most of the market requirements are occupied by the RV speed reducer and the harmonic speed reducer which are high in price and high in price. Usually the gear will reach than higher transmission ratio the case, the driven wheel of drive wheel must accord with the multiple relation of diameter number of teeth to the conventional structure of gear requires the minimum number of teeth of gear must satisfy a definite value, and these often lead to driven wheel number of teeth diameter too big, and again or through the mode of multistage cascade, the speed reducer after the multistage cascade is heavy, can't satisfy the robot and slow down self structure and will be little extra requirement such as light.
Disclosure of Invention
Aiming at the problems that the prior gear accelerating transmission structure has to meet the multiple relation of diameter and tooth number when reaching higher transmission ratio, the diameter of the tooth number of a driven wheel is overlarge, a multi-stage cascade structure is heavy and the like, the invention provides the gear accelerating transmission structure. The specific technical scheme is as follows:
a gear acceleration transmission structure comprises an input assembly and an output assembly, wherein the output assembly comprises an output eccentric wheel and more than one output gear which is arranged on the circumferential surface of the output eccentric wheel and is attached to the output eccentric wheel, and the output eccentric wheel is an eccentric wheel. The output gear is adopted to drive the output eccentric wheel to rotate, so that the purpose of accelerating transmission is achieved.
Preferably, any point M (x) in the eccentric profile curve of the output geart，yt) The following formula is satisfied:
Figure BDA0002815632180000021
Figure BDA0002815632180000022
wherein, the center of the output gear is the origin, t is (0, 2N)1π]N1 is the number of output gear teeth, N1 is an integer greater than 1, A is the axle center distance of two wheels, and B1 is the eccentricity of the output eccentric wheel.
Preferably, the profile curve of the output gear is obtained by taking an equidistant curve with the radius of the output eccentric wheel from the inner side of the profile curve of the output gear.
Preferably, each output eccentric wheel is attached to a curve corresponding to one tooth on the output gear, and the outer circumferential surface of each output eccentric wheel is in rolling connection with different positions on the curve of the corresponding tooth. In the process that the output eccentric wheel is in contact with the gear corresponding to the output gear, the output eccentric wheel rotates for N1 circles when the output gear rotates for one circle, and then the output eccentric wheel is engaged with the curve corresponding to the next tooth on the output gear and is driven to rotate by the curve, so that the purpose of accelerating transmission is achieved.
Preferably, the number of teeth N1 of the output gear is 3-21 teeth.
Preferably, the number of teeth N1 of the output gear is 4-8 teeth.
Preferably, the number of teeth N1 of the output gear is 8 teeth.
Preferably, the transmission structure further comprises a mounting plate, and the input assembly and the output assembly are respectively mounted on two side surfaces of the mounting plate.
Preferably, the input assembly comprises an input gear and more than one input eccentric which is uniformly distributed in the circumferential direction of the input gear and is matched with the outer circumferential profile of the input gear, and each input eccentric rotating shaft is rigidly and coaxially connected with one output gear central shaft. The input gear divergently drives the input eccentric wheel to form a stable single-stage driving structure, then the input eccentric wheel is gathered again through the output gear and drives the output eccentric wheel to rotate, so that a complete two-stage transmission driving structure is formed, and the whole transmission process with a large transmission ratio is completed through two transmissions.
Preferably, the eccentric profile of the input gearAny point M in the curve2(xt，yt) The following formula is satisfied:
Figure BDA0002815632180000023
Figure BDA0002815632180000031
wherein, the input gear center is the origin, t ═ 0, 2N2π]N2 is the number of teeth of the input gear, N2 is an integer greater than 1, A is the axle center distance of two wheels, and B2 is the eccentricity of the input eccentric wheel.
Preferably, the input gear profile curve is obtained by taking an equidistant curve inward from the eccentric profile curve of the input gear by the radius of the input eccentric.
Preferably, the input gear tooth count N2 is 3-21 teeth.
Preferably, the input gear tooth count N2 is 4-8 teeth.
Preferably, the input gear tooth number N2 is 8 teeth.
Preferably, the input gear tooth number N2 is equal to the output gear tooth number N1.
Preferably, the output assembly comprises an output eccentric wheel set formed by overlapping W1 output eccentric wheels with a central shaft, and more than one output gear set arranged in the circumferential direction of the output eccentric wheel set, each output gear set is formed by rigidly and coaxially connecting W1 output gears, and W1 is an integer greater than or equal to 2;
and each layer of output gears in the output gear set are uniformly distributed in the direction of the outer circumference of the output eccentric wheel of the corresponding layer in the output eccentric wheel set and are attached to the outline of the outer circumference of the output eccentric wheel of the corresponding layer.
Preferably, the number of output gears W1 in the output gear set is 3-6.
Preferably, the number of output gears W1 in the output gear set is 4.
PreferablyThe position of the output gear group in the circumferential direction of the output gear positioned below from top to bottom is that the output gear positioned above rotates clockwise around a central shaft
Figure BDA0002815632180000032
And obtaining the compound.
Preferably, the position of the output gear set in the circumferential direction of the output gear positioned below from top to bottom is that the output gear positioned above rotates anticlockwise around a central shaft
Figure BDA0002815632180000033
And obtaining the compound.
Preferably, N1 output gear sets are uniformly distributed in the circumferential direction of each output eccentric gear set.
Preferably, each of the output eccentric wheel sets is provided with 1 output gear set in a circumferential direction.
Preferably, 4-8 output gear sets are uniformly distributed in the circumferential direction of the output eccentric gear set.
Preferably, 6 output gear sets are uniformly distributed in the circumferential direction of the output eccentric gear set.
Preferably, the input assembly comprises an input gear set formed by superposing W2 input gears with a central shaft and more than one input eccentric gear set arranged in the circumferential direction of the input gear set, each input eccentric gear set is formed by coaxially connecting W2 input gear sets, and W2 is an integer greater than or equal to 2;
and each layer of input gear in the input gear set is arranged on the outer circumferential surface of the input gear of the corresponding layer in the input gear set and is attached to the outer circumferential contour of the input gear of the corresponding layer.
Preferably, the number of input gears W2 in the input gear set is 3-6.
Preferably, the number of input gears W2 in the input gear set is 4.
Preferably, the circumferential position of the input gear set positioned below from top to bottom isThe input gear located above rotates clockwise around the central shaft
Figure BDA0002815632180000041
And obtaining the compound.
Preferably, the circumferential position of the input gear positioned below the input gear set from top to bottom is that the input gear positioned above rotates counterclockwise around a central shaft
Figure BDA0002815632180000042
And obtaining the compound.
Preferably, each input eccentric wheel consists of an input eccentric wheel main body and a first rolling bearing sleeved on the periphery of the input eccentric wheel main body, and the outer diameter of the first rolling bearing is equal to the diameter of the input eccentric wheel; the output eccentric wheel is composed of an output eccentric wheel main body and a second rolling bearing sleeved on the periphery of the output eccentric wheel main body, and the outer diameter of the second rolling bearing is equal to the diameter of the output eccentric wheel.
The accelerating machine obtained by adopting the gear transmission structure has the advantages that the diameter sizes of the driving gear and the driven gear 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 mode, 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.
Has the advantages that:
the technical scheme of the invention has the following beneficial effects:
(1) each output eccentric wheel is attached to a curve corresponding to one tooth on the output gear, and the outer circumferential surface of each output 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 that the output eccentric wheel is in contact with the gear corresponding to the output gear, the output eccentric wheel rotates for N1 circles when the output gear rotates for one circle, and then the output eccentric wheel is engaged with the curve corresponding to the next tooth on the output gear and is driven to rotate by the curve, so that the purpose of accelerating transmission is achieved.
(2) The output gear set formed by overlapping a plurality of output gears is adopted for transmission, the contact parts of the concave-convex edges of the output gears on different layers in the same output gear set and the corresponding output eccentric wheels are different, the transmission stability between the output eccentric wheel set and the output gear set is greatly improved, and the stable and smooth transmission of the output eccentric wheel set by the output gear set is realized.
(3) The input gear divergently drives the input eccentric wheel to form a stable single-stage driving structure, then the input eccentric wheel is gathered again through the output gear and drives the output eccentric wheel to rotate, so that a complete two-stage transmission driving structure is formed, and the whole transmission process with a large transmission ratio is completed through two transmissions.
(4) The accelerating structure obtained by adopting the gear accelerating transmission structure has the advantages that the diameter sizes of the driving gear and the driven gear can be approximately the same, when the N times of gears drive one tooth gear to rotate, the periphery of the driving gear can simultaneously drive a plurality of one tooth gears in a surrounding manner, and the problem that when the traditional single-stage transmission gear ratio is used for gear transmission, the periphery of the N times of gears cannot simultaneously drive a plurality of large gears on the same plane due to insufficient space 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.
(5) The structure of the output eccentric wheel and the structure of the input eccentric wheel are extremely simplified, the structure of the output eccentric wheel and the structure of the input eccentric wheel are eccentric wheels, 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.
(6) The input gear and the output gear are of polygonal structures with concave edges, are completely different from the existing gear tooth structure in shape, can be directly processed by wire cutting and slow-moving wires, are low in manufacturing cost, are matched with an eccentric driving wheel complete set structure with a simple structure, and can be manufactured at a low cost, so that the manufactured accelerating machine has a proper economic value.
(7) The output eccentric wheel and the input eccentric wheel are circular and can be seen as only one tooth, and in order to realize continuous transmission of the output gear and the input gear, a multi-layer overlapping structure is required.
(8) The transmission between the input gear and the input eccentric wheel and the transmission between the output gear and the output eccentric wheel are 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.
(9) In practical application, the kneading mode is different according to the length relation between the circumference of the output eccentric wheel and a section of profile curve corresponding to the output gear. When the circumference of the output eccentric wheel is equal to the length between a section of profile curve corresponding to the output gear, each point of contact is just in a rolling static friction state; when the circumference of the output eccentric wheel is larger than the length of a section of contour curve corresponding to the output gear, namely the length of the output eccentric wheel which rotates for one circle is larger than the length of one section of contour curve of the output gear, the output gear is suitable to be driven; when the circumference of the output eccentric wheel is smaller than the length of a section of contour curve corresponding to the output gear, namely the length of the output eccentric wheel which rotates for one circle is smaller than the length of one section of contour curve of the output gear, the output gear can also be used as a driving wheel to drive the output eccentric wheel to rotate, namely the output gear can be driven from the output end to the input end to achieve the purpose of acceleration.
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 perspective view of a preferred gear transmission structure of the present invention;
FIG. 2 is a perspective view of a preferred gear transmission structure of the present invention;
FIG. 3 is a perspective view of a preferred gear transmission structure of the present invention;
FIG. 4 is a schematic diagram of the eccentric profile of the preferred output gear of the present invention;
FIG. 5 is a schematic diagram of the eccentric profile of the preferred input gear of the present invention;
FIG. 6 is a schematic diagram of a preferred 2-fold transmission acceleration structure of the present invention;
FIG. 7 is a schematic diagram of a preferred 3-fold transmission acceleration structure of the present invention;
FIG. 8 is a schematic diagram of a preferred 4-fold transmission acceleration structure of the present invention;
FIG. 9 is a schematic diagram of a preferred 5-fold transmission acceleration structure of the present invention;
FIG. 10 is a schematic diagram of a preferred 6-fold transmission acceleration structure of the present invention;
FIG. 11 is a schematic diagram of a preferred 8-fold transmission acceleration structure of the present invention;
FIG. 12 is a schematic view of a preferred 10-fold transmission acceleration structure of the present invention;
FIG. 13 is a schematic diagram of a preferred 14 times transmission acceleration structure of the present invention;
FIG. 14 is a schematic diagram of a preferred output assembly of the present invention including 2 output gears;
FIG. 15 is a schematic diagram of a preferred output assembly of the present invention including 3 output gears;
FIG. 16 is a schematic diagram of a preferred output assembly of the present invention including 4 output gears;
FIG. 17 is a schematic view of a preferred output assembly of the present invention including 5 output gears;
FIG. 18 is a schematic view of a preferred output assembly of the present invention including 6 output gears;
FIG. 19 is a schematic diagram of a preferred output assembly of the present invention including 7 output gears;
FIG. 20 is a schematic diagram of a preferred output assembly of the present invention including 8 output gears;
FIG. 21 is a schematic view of a preferred output assembly of the present invention including 9 output gears;
FIG. 22 is a schematic diagram of a preferred output assembly of the present invention including 10 output gears.
In the figure: 1. an input component; 11. inputting an eccentric wheel set; 12. an input gear set; 101. inputting an eccentric wheel; 102. an input gear; 103. an input gear eccentric profile curve; 104. inputting a gear profile curve; 2. an output component; 21. an output eccentric wheel set; 22. an output gear set; 201. an output eccentric wheel; 202. an output gear; 203. an output gear eccentric profile curve; 204. outputting a gear profile curve; 211. an output eccentric wheel main body; 212. a second rolling bearing; 3. and (7) mounting a disc.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present invention more apparent, the technical solutions of the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings of the embodiments of the present invention, and it is obvious that the described embodiments are some, but not all embodiments of the present invention. All other embodiments, which can be obtained by a person skilled in the art without any inventive step based on the embodiments of the present invention, are within the scope of the present invention. Thus, the following detailed description of the embodiments of the present invention, presented in the figures, is not intended to limit the scope of the invention, as claimed, but is merely representative of selected embodiments of the invention. All other embodiments, which can be obtained by a person skilled in the art without any inventive step based on the embodiments of the present invention, are within the scope of the present invention.
The gear acceleration transmission structure in the embodiment utilizes the matching between more than two groups of gears, is not limited by the relation of tooth number and diameter, can keep the size of the gear from being synchronously enlarged under the condition of realizing large transmission ratio, and even finally enables the transmission ratio to be unrelated with the size ratio of the gear, thereby achieving the purpose of high-power transmission. The specific implementation content is as follows:
as shown in fig. 1 to 3, a gear acceleration transmission structure comprises an input assembly 1 and an output assembly 2, wherein the output assembly 2 comprises an output eccentric 201 and more than one output gears 202 arranged on the circumferential surface of the output eccentric 201 and jointed with the output eccentric 201, and the output eccentric 201 is an eccentric. The output gear 202 is adopted to drive the output eccentric wheel 201 to rotate, so that the purpose of accelerating transmission is achieved.
As a preferred embodiment, as shown in FIG. 4, any point M (x) in the eccentric profile curve 203 of the output geart，yt) The following formula is satisfied:
Figure BDA0002815632180000071
Figure BDA0002815632180000081
where the center of the output gear 202 is the origin, and t is (0, 2N)1π]N1 is the number of teeth of the output gear 202, N1 is an integer greater than 1, a is the axial distance of two wheels, and B1 is the eccentricity of the output eccentric 201.
In a preferred embodiment, the output gear contour curve 204 is obtained by the eccentric contour curve 203 of the output gear being spaced inward by an equidistant curve of the radius R1 of the output eccentric 201.
In a preferred embodiment, each output eccentric 201 fits a curve corresponding to a tooth on the output gear 202, and the outer circumferential surface of the output eccentric 201 contacts and is in rolling connection with different positions on the curve of the corresponding tooth. In the process that the output eccentric wheel 201 is in contact with the gear corresponding to the output gear, every time the output gear 202 rotates for one circle, the output eccentric wheel 201 rotates for N1 circles, and then the output eccentric wheel 201 is engaged with the curve corresponding to the next tooth on the output gear 202 and is driven to rotate by the curve, so that the purpose of accelerating transmission is achieved.
The output gear contour curve 204 obtained by adopting the formula can enable the outer circumferential surface of the output eccentric wheel 201 and the output gear 202 to be always in a fit state, and the output eccentric wheel 201 and the output gear 202 are in rubbing transmission.
In a preferred embodiment, as shown in fig. 7-13, the number of teeth N1 of the output gear 202 is 3-21.
In a preferred embodiment, the number of teeth N1 of the output gear 202 is 4-8.
In a preferred embodiment, the number of teeth N1 of the output gear 202 is 8.
As a preferred embodiment, the transmission structure further comprises a mounting plate, and the input assembly 1 and the output assembly 2 are respectively mounted on two side surfaces of the mounting plate.
In a preferred embodiment, the input assembly 1 comprises an input gear 102 and more than one input eccentric 101 uniformly distributed in the circumferential direction of the input gear 102 and conforming to the outer circumferential profile of the input gear 102, and each input eccentric 101 rotating shaft is rigidly and coaxially connected with the central shaft of one output gear 202. The input gear 102 divergently drives the input eccentric wheel 101 to form a stable single-stage driving structure, then the input eccentric wheel 101 is gathered again through the output gear 202 and is driven inwards and backwards to drive the output eccentric wheel 201 to rotate, a complete two-stage transmission driving structure is formed, and the whole transmission process with a large transmission ratio is completed through two transmissions.
In a preferred embodiment, any point M in the eccentric profile 103 of the input gear is2(xt，yt) The following formula is satisfied:
Figure BDA0002815632180000091
Figure BDA0002815632180000092
where the center of the input gear 102 is the origin, and t is (0, 2N)2π]N2 is the number of teeth of the input gear 102, N2 is an integer greater than 1, a is the axial distance of two wheels, and B2 is the eccentricity of the input eccentric 101.
In a preferred embodiment, the input gear profile 104 is the curve of the eccentric profile 103 of the input gear that is equidistant inward from the radius R3 of the input eccentric 101.
As a preferred embodiment, the number of the input eccentric wheels 101 distributed in the circumferential direction of the input gear 102 can be controlled according to the requirement, and the occupation space of the input eccentric wheels 101 on the outer circumferential surface of the input gear 102, the transmission stability, the transmission efficiency and the like are comprehensively considered, and several preferred schemes are adopted.
In a preferred embodiment, the number of teeth N2 of the input gear 102 is 3-21.
In a preferred embodiment, the number of teeth N2 of the input gear 102 is 4-8.
In a preferred embodiment, the number N2 of teeth of the input gear 102 is 8.
In practice, it has been found that the transmission efficiency is relatively good when the number of teeth N1 of the input gear 102 is 8.
The input gear 102 receives the least frictional force of the input eccentric 101 when the circumferential profile surface of the input eccentric 101 is in contact with the concave center of each tooth of the input gear 102, and the input gear 102 receives the most frictional force of the input eccentric 101 when the circumferential profile surface of the input eccentric 101 is in contact with the convex center of each tooth of the input gear 102.
It is easily understood that the concave-convex effect of the circumferential surface profile of the input gear 102 is more pronounced as the eccentricity B2 of the input eccentric 101 is larger.
In order to ensure the uniformity of the force applied to the input gear 102 by the input eccentric 101 during the operation, when the circumferential profile surface of a certain input eccentric 101 is at the concave center position of the teeth on the input gear 102, if the number of teeth of the input gear 102 is odd, the circumferential profile surface of the input eccentric 101 opposite to the surface is in contact with the convex center of the teeth on the input gear 102; if the number of teeth of the input gear 102 is even, two input eccentric wheels 101 are arranged on the opposite left side and the opposite right side of the input 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 input eccentrics 101 has a certain correlation with the number of teeth of the input gear 102, half or equal to the number of teeth of the input gear 102, preferably half of the number of teeth of the input gear 102, for example, when the number of teeth of the input gear 102 is 8, the number of the input eccentrics 101 is preferably 4; if the number of teeth of the input gear 102 is 6, the number of the input eccentrics 101 may be 3 or 6.
In a preferred embodiment, the number of teeth N2 of the input gear 102 is equal to the number of teeth N1 of the output gear 202.
As a preferred embodiment, the output assembly 2 comprises an output eccentric wheel set 21 formed by superposing W1 output eccentric wheels 201 on a central shaft, and more than one output gear set 22 arranged in the circumferential direction of the output eccentric wheel set 21, each output gear set 22 is formed by rigidly and coaxially connecting W1 output gears 202, and W1 is an integer greater than or equal to 2;
each layer of the output gears 202 in the output gear set 22 is uniformly distributed in the direction of the outer circumference of the output eccentric wheel 201 of the corresponding layer in the output eccentric gear set 21 and is fitted with the outer circumference of the output eccentric wheel 201 of the corresponding layer.
In a preferred embodiment, the number W1 of the output gears 202 in the output gear set 22 is 3-6.
In a preferred embodiment, the number W1 of the output gears 202 in the output gear set 22 is 4.
In the test process, when the number W1 of the input gears 102 in the input gear set 12 is 4, the transmission stability is better.
The input gear set 12 formed by overlapping a plurality of input gears 102 is adopted for transmission, and the contact parts of the concave-convex edges on the input gears 102 on different layers in the same input gear set 12 and the corresponding input eccentric wheels 101 are different, so that the transmission stability between the input eccentric wheel set 11 and the input gear set 12 is greatly improved, and the stable and smooth transmission of the input eccentric wheel set 11 by the input gear set 12 is realized.
In a preferred embodiment, the position of the output gear set 22 in the circumferential direction of the output gear 202 located at the lower position from top to bottom is such that the output gear 202 located at the upper position rotates clockwise around the central axis
Figure BDA0002815632180000101
And obtaining the compound.
In a preferred embodiment, the position of the output gear set 22 in the circumferential direction of the output gear 202 located at the lower position from top to bottom is such that the output gear 202 located at the upper position rotates counterclockwise around the central axis
Figure BDA0002815632180000102
And obtaining the compound.
In a preferred embodiment, N1 output gear sets 22 are uniformly distributed in the circumferential direction of each output eccentric gear set 21.
In a preferred embodiment, 1 output gear set 22 is disposed in a circumferential direction of each output eccentric gear set 21.
In a preferred embodiment, 4 to 8 output gear sets 22 are uniformly distributed in the circumferential direction of the output eccentric wheel set 21.
In a preferred embodiment, 6 output gear sets 22 are uniformly distributed in the circumferential direction of the output eccentric wheel set 21.
As a preferred embodiment, the input assembly 1 includes an input gear set 12 formed by superposing W2 input gears 102 on a central shaft, and more than one input eccentric gear set 11 arranged in the circumferential direction of the input gear set 12, each input eccentric gear set 11 is formed by coaxially connecting W2 input gear sets 12, and W2 is an integer greater than or equal to 2;
each layer of the input gears 102 in the input gear set 12 is arranged on the outer circumferential surface of the input gear 102 of the corresponding layer in the input gear set 12 and is attached to the outer circumferential profile of the input gear 102 of the corresponding layer.
In a preferred embodiment, the number of input gears 102 in the input gear set 12, W2, is 3-6.
In a preferred embodiment, the number W2 of the input gears 102 in the input gear set 12 is 4.
As a preferred embodiment, the input gear set 12 the circumferential position of the input gear 102 located downward from the top is such that the input gear 102 located upward rotates clockwise around the central axis
Figure BDA0002815632180000111
And obtaining the compound.
In a preferred embodiment, the circumferential position of the input gear 102 of the input gear set 12 located at the lower position from top to bottom is such that the input gear 102 located at the upper position rotates counterclockwise around the central axis
Figure BDA0002815632180000112
And obtaining the compound.
As a preferred embodiment, each of the input eccentrics 101 is composed of an input eccentric body and a first rolling bearing (not shown) sleeved on the periphery of the input eccentric body, and the outer diameter of the first rolling bearing is equal to the diameter of the input eccentric 101; the output eccentric wheel 201 is composed of an output eccentric wheel main body 211 and a second rolling bearing 212 sleeved on the periphery of the output eccentric wheel main body 211, and the outer diameter of the second rolling bearing 212 is equal to the diameter of the output eccentric wheel 211.
As shown in fig. 6-13, the output assembly 2 has 2, 3, 4, 5, 6, 8, 10, 14 output gears 202 with teeth, the output eccentric wheel 201 fits to a curve corresponding to a tooth on each output gear 202, and the outer circumferential surface of the output eccentric wheel 201 contacts with different positions on the curve corresponding to the tooth and is in rolling connection. During the process that the output gear 202 is in contact with the corresponding output eccentric wheel 201, every time the output gear 202 rotates for one circle, each output eccentric wheel 201 rotates for N1 circles, therefore, when the number of the output gear teeth is 2, 3, 4, 5, 6, 8, 10, 14, the output gear 202 rotates for one circle, the output eccentric wheel 201 rotates for 2, 3, 4, 5, 6, 8, 10, or 14 circles, and the purpose of accelerating transmission is achieved.
When the double-gear transmission mechanism is applied, the input gear 102 is controlled to divergently drive the input eccentric wheel 101 to form a stable single-stage driving structure, then the input eccentric wheel 101 is gathered again through the output gear 202 and drives the output eccentric wheel 201 to rotate, a complete two-stage transmission driving structure is formed, and the whole transmission process of the accelerating machine with a large transmission ratio is completed through two transmissions. At this time, the rotation speed of the output eccentric wheel 201 is the rotation speed of the input gear 102 (N1 × N2), two transmissions complete the acceleration transmission process with large transmission ratio, and according to the requirement of the transmission ratio, the secondary gear transmission in the invention can be changed into three-stage or four-stage transmission, etc., so that the space occupied by the transmission structure is greatly saved.
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 (10)

1. The gear acceleration transmission structure is characterized by comprising an input assembly and an output assembly, wherein the output assembly comprises an output eccentric wheel and more than one output gear which is arranged on the circumferential surface of the output eccentric wheel and is jointed with the output eccentric wheel.
2. A geared acceleration transmission structure according to claim 1, characterized by the fact that any point M (x) in the eccentric profile curve of the output geart，yt) The following formula is satisfied:
Figure FDA0002815632170000011
Figure FDA0002815632170000012
wherein, the center of the output gear is the origin, t is (0, 2N)1π]N1 is the number of output gear teeth, N1 is an integer greater than 1, A is the axle center distance of two wheels, and B1 is the eccentricity of the output eccentric wheel.
3. A gear acceleration transmission arrangement according to claim 2, characterized in that the profile curve of the output gear is obtained by inward-taking the curve of the profile of the output gear as the equidistant curve of the output eccentric radius.
4. The overdrive gearing structure according to claim 3, wherein the number of teeth N1 of said output gear is 3-21.
5. The overdrive gearing structure according to claim 3, wherein the number of teeth N1 of said output gear is 4-8.
6. The overdrive gearing structure according to claim 3, wherein the number of teeth N1 of said output gear is 8.
7. The geared acceleration transmission structure of any one of claims 1-6, wherein the transmission structure further comprises a mounting plate, and the input assembly and the output assembly are mounted on two sides of the mounting plate, respectively.
8. A gear acceleration transmission arrangement according to any one of claims 1-6, characterized by, that the input assembly includes an input gear and more than one input eccentric evenly distributed in the circumferential direction of the input gear and following the outer circumferential profile of the input gear, each input eccentric rotation shaft being rigidly and coaxially connected with one of the output gear central shafts.
9. A geared acceleration transmission structure according to claim 8, characterized by the fact that any point M in the eccentric profile curve of the input gear2(xt，yt) The following formula is satisfied:
Figure FDA0002815632170000021
Figure FDA0002815632170000022
wherein, the input gear center is the origin, t ═ 0, 2N2π]N2 is the number of teeth of the input gear, N2 is an integer greater than 1, A is the axle center distance of two wheels, and B2 is the eccentricity of the input eccentric wheel.
10. A geared accelerating drive according to claim 9, wherein the input gear profile curve is obtained by an equidistant curve inward of the input gear profile curve by the radius of the input eccentric.
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