CN113007285A - Differential gear transmission mechanism - Google Patents
Differential gear transmission mechanism Download PDFInfo
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- CN113007285A CN113007285A CN202110212127.XA CN202110212127A CN113007285A CN 113007285 A CN113007285 A CN 113007285A CN 202110212127 A CN202110212127 A CN 202110212127A CN 113007285 A CN113007285 A CN 113007285A
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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
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
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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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/28—Counterweights, i.e. additional weights counterbalancing inertia forces induced by the reciprocating movement of masses in the system, e.g. of pistons attached to an engine crankshaft; Attaching or mounting same
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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
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
- F16H2001/327—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear with orbital gear sets comprising an internally toothed ring gear
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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
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
- F16H2001/328—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear comprising balancing means
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Abstract
The invention discloses a differential gear transmission mechanism, which comprises an eccentric wheel, a first internal gear, a second internal gear, a first external gear, a second external gear and an input shaft, wherein the eccentric wheel is arranged on the input shaft; the first internal gear and the second internal gear are fixedly connected and coaxial; the input shaft is used for driving the eccentric wheel to do eccentric motion; the outer side surface of the eccentric wheel is used for pushing the first internal gear and the second internal gear to do first circular motion along the axis of the input shaft; the first internal gear and the second internal gear are in sliding fit with the outer side face of the eccentric wheel; the first internal gear is meshed with the first external gear; the second internal gear is meshed with the second external gear; the invention has simple structure, and can achieve the purposes of simplifying the structure and lightening the weight while ensuring the transmission ratio through the structural design.
Description
Technical Field
The invention relates to the technical field of speed reducers, in particular to a differential gear transmission mechanism.
Background
The differential gear transmission is a transmission mode widely applied to various industrial fields, and along with the development of production technology and the development requirements of high-quality products, especially the development requirements of automatic products such as robots and the like, the existing transmission device has the advantages of complex structure, small transformation ratio, more accessories and large occupied space, and cannot meet the requirements of structure simplification and light weight.
Disclosure of Invention
The invention aims to provide a differential gear transmission mechanism which can achieve the purposes of simplifying the structure and lightening the weight while ensuring the transmission ratio through structural design.
The invention is realized by the following technical scheme:
a differential transmission mechanism comprises an eccentric wheel, a first internal gear, a second internal gear, a first external gear, a second external gear and an input shaft; the first internal gear is fixedly connected with the second internal gear; the input shaft is used for driving the eccentric wheel to do eccentric motion; when the input shaft drives the eccentric wheel to move, the outer side face of the eccentric wheel is used for pushing the first internal gear and the second internal gear to do first circular motion along the axis of the input shaft; the first internal gear and the second internal gear are in sliding fit with the outer side face of the eccentric wheel; the first internal gear is meshed with the first external gear; the second internal gear is meshed with the second external gear; when the first inner gear moves, the first outer gear is fixed and does not rotate; when the first inner gear moves, the first outer gear is fixed and does not rotate; the first internal gear and the first external gear are matched with each other, so that the first internal gear can do second circular motion along the axis of the eccentric wheel; the second external gear can be driven to rotate by the second internal gear.
Preferably, the input shaft is fixedly connected with the eccentric wheel.
Preferably, the eccentric wheel is connected with the first internal gear and the second internal gear through bearings.
As a further aspect of the present invention, the first internal gear and the second internal gear are both cycloid gears.
Preferably, the first external gear includes a plurality of first pin teeth, and the plurality of first pin teeth are engaged with the first internal gear; the second external gear comprises a pin gear plate and a plurality of second pin teeth, the pin gear plate is provided with a through hole used for installing the second pin teeth, and the second pin teeth are meshed with the second internal gear.
Preferably, the number of teeth of the first internal gear is at least one less than that of the first needle teeth; the number of the teeth of the second internal gear is at least one less than that of the second needle teeth.
As a further aspect of the present invention, the first internal gear and the second internal gear are both involute gears.
Preferably, the first external gear and the second external gear are both ring gears having internal teeth; the first internal gear and the second internal gear have external teeth that mesh with the first external gear and the second external gear, respectively.
Preferably, the number of teeth of the first internal gear is at least two less than the number of teeth of the internal teeth of the first external gear; the number of teeth of the second internal gear is at least two less than that of the teeth of the second external gear.
As a further technical scheme of the invention, the device also comprises a balance weight component for eliminating eccentric vibration, wherein the balance weight component comprises a connecting rod and a balance weight, one end of the connecting rod is connected with the balance weight, and the other end of the connecting rod is connected with the input shaft.
In the existing K-H-V type planetary gear train with small tooth difference, it includes a sun gear (denoted by K), a planet carrier (denoted by H) and an output shaft (denoted by V) with an output mechanism. The planet carrier H is a driving part, the planet wheel (indicated by G) is a driven part, the output motion is the rotation of the planet wheel, the rotation is converted into the output shaft through the conversion device and transmitted, the pressure of the outer gear, the planet carrier H (eccentric wheel) and the output conversion structure V is applied to the inner gear in the traditional K-H-V structure, the stress points of the three types of force are far, and the requirement that the integral strength of the inner gear is high and the weight is large is met.
Compared with the prior art, the invention has the following advantages and beneficial effects:
1. the embodiment of the invention relates to a differential gear transmission mechanism, which directly combines two sets of planet carriers H (namely eccentric wheels) as input by omitting two sets of output conversion devices V with two-stage K-H-V structures, and fixedly connects two sets of internal gears as output and input transmission between two stages in series connection, thereby not only ensuring the reduction ratio, but also achieving the purpose of structure simplification;
2. the embodiment of the invention relates to a differential gear transmission mechanism, which realizes the expansion of the inner diameters of a first internal gear and a second internal gear by omitting two sets of output conversion devices V with two-stage K-H-V structures, thereby realizing the expansion of the inner diameters and the outer diameters of an input shaft and an eccentric wheel, increasing the inner holes of the whole transmission mechanism and realizing the light weight of the structure. The ratio of the reduction ratio to the weight, the ratio of the transmission torque to the weight, and the ratio of the transmission power to the weight are greatly increased;
3. the embodiment of the invention relates to a differential gear transmission mechanism, which omits the pressure of an output conversion structure V, directly and fixedly connects two sets of internal gears to ensure that the stress points of the two sets of internal gears are very close, the internal diameter of the internal gears is enlarged to ensure that the internal gears are drawn close by the distance of a planet carrier H (eccentric wheel), the distance of each stress point is small, the strength of the whole internal gear is not required to be high, the weight of the internal gear is further lightened, and the structural strength is optimized;
4. the embodiment of the invention relates to a differential gear transmission mechanism, which can effectively solve the problem of eccentric vibration and improve the stability of a transmission assembly by arranging a balance block assembly.
Drawings
The accompanying drawings, which are included to provide a further understanding of the embodiments of the invention and are incorporated in and constitute a part of this application, illustrate embodiment(s) of the invention and together with the description serve to explain the principles of the invention. In the drawings:
FIG. 1 is a schematic structural diagram of an embodiment of the present invention;
FIG. 2 is an exploded view of an embodiment of the present invention;
FIG. 3 is a schematic structural diagram of another embodiment of the present invention;
FIG. 4 is a schematic view of the first internal gear, the second internal gear, the eccentric wheel and the input shaft of another embodiment of the present invention;
FIG. 5 is a schematic structural diagram of a balancing block assembly according to an embodiment of the present invention;
FIG. 6 is a top view of a plurality of eccentrics of an embodiment of the present invention.
The gear comprises a 1-eccentric wheel, a 2-first internal gear, a 3-second internal gear, a 4-first external gear, a 41-first pin gear, a 5-second external gear, a 51-pin gear disc, a 52-second pin gear, a 6-input shaft, a 7-balance block assembly, a 71-connecting rod and a 72-balance block.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention is further described in detail below with reference to examples and accompanying drawings, and the exemplary embodiments and descriptions thereof are only used for explaining the present invention and are not meant to limit the present invention.
In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention. However, it will be apparent to one of ordinary skill in the art that: it is not necessary to employ these specific details to practice the present invention. In other instances, well-known structures, circuits, materials, or methods have not been described in detail so as not to obscure the present invention.
Throughout the specification, reference to "one embodiment," "an embodiment," "one example," or "an example" means: the particular features, structures, or characteristics described in connection with the embodiment or example are included in at least one embodiment of the invention. Thus, the appearances of the phrases "one embodiment," "an embodiment," "one example" or "an example" in various places throughout this specification are not necessarily all referring to the same embodiment or example. Furthermore, the particular features, structures, or characteristics may be combined in any suitable combination and/or sub-combination in one or more embodiments or examples. Further, those of ordinary skill in the art will appreciate that the illustrations provided herein are for illustrative purposes and are not necessarily drawn to scale. As used herein, the term "and/or" includes any and all combinations of one or more of the associated listed items.
In the description of the present invention, it is to be understood that the terms "front", "rear", "left", "right", "upper", "lower", "vertical", "horizontal", "high", "low", "inner", "outer", etc. indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of description and simplicity of description, and do not indicate or imply that the referenced devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and therefore, are not to be construed as limiting the scope of the present invention.
Examples
As shown in fig. 1, in one embodiment of the present application, there is provided a differential gear mechanism including an eccentric wheel 1, a first internal gear 2, a second internal gear 3, a first external gear 4, and a second external gear 5, an input shaft 6; the first internal gear 2 and the second internal gear 3 are fixedly connected and coaxial; the input shaft 6 is used for driving the eccentric wheel 1 to do eccentric motion; when the input shaft 6 drives the eccentric wheel 1 to move, the outer side surface of the eccentric wheel 1 is used for pushing the first internal gear 2 and the second internal gear 3 to do a first circular motion along the axis of the input shaft 6; the first internal gear 2 and the second internal gear 3 are in sliding fit with the outer side face of the eccentric wheel 1; the first internal gear 2 is meshed with the first external gear 4; the second internal gear 3 is meshed with the second external gear 5; when the first internal gear 2 moves, the first external gear 4 is fixed and does not rotate; when the first internal gear 2 moves, the first external gear 4 is fixed and does not rotate; the first internal gear 2 and the first external gear 4 are matched with each other, so that the first internal gear 2 performs second circular motion along the axis of the eccentric wheel 1; the second external gear 5 can be driven to rotate by the second internal gear 3.
In the embodiment, the first internal gear 2 and the second internal gear 3 are fixedly connected, the input shaft 6 is used as an external input, the input shaft 6 drives the eccentric wheel 1, and the first internal gear 2 and the second internal gear 3 are driven to do a first circular motion along the axis of the input shaft 6 through the eccentric action of the eccentric wheel 1; the first external gear 4 is fixed when the first internal gear 2 moves and is meshed with the first internal gear 2, so that the first internal gear 2 is driven to do second circular motion along the axis of the first internal gear 2; because the first internal gear 2 and the second internal gear 3 are fixedly connected, the second internal gear 3 is driven to do second circular motion along the axis of the second internal gear 3 while the first internal gear 2 does second circular motion, so that the second internal gear 3 drives the second external gear 5 to move, and the second external gear 5 is used as an output end to realize transmission; this differential gear drive mechanism carries out configuration optimization through the structure, when guaranteeing transmission efficiency, has realized the purpose of simplified structure and lightweight.
Wherein, through setting up the eccentric wheel 1, eccentric wheel 1 is eccentric motion under the effect of input shaft 6, namely eccentric wheel 1 is circular motion along the axis of input shaft 6, the lateral surface of eccentric wheel 1 promotes first internal gear 2 and second internal gear 3 and does the first circular motion along the axis of input shaft 6 at the same time, and because the lateral surface of eccentric wheel 1 and first internal gear 2 and second internal gear 3 are all cooperated, while first internal gear 2 does the first circular motion, first internal gear 2 meshes with first external gear 4, thus realize that first internal gear 2 does the second circular motion along the axis of eccentric wheel 1, through the setting of eccentric wheel 1, realize simultaneously that first internal gear 2 does two kinds of different circular motions, and because first internal gear 2 and second internal gear 3 are fixed connection, second internal gear 3 moves along with first internal gear 2 simultaneously, the axes and the motion directions of the two different circular motions are different; the first internal gear 2 and the second internal gear 3 are fixedly connected, so that the first internal gear 2 directly drives the second internal gear 3, the first-stage transmission to the second-stage transmission of the transmission assembly is realized, the output conversion devices are reduced in a fixed connection mode, the structure of the whole transmission assembly is simplified, the first internal gear 2 and the second internal gear 3 are fixedly connected, the output conversion devices are reduced, the input devices are reduced, and the input of the whole transmission mechanism can be realized only through one input device; the inner diameters of the first inner gear 2 and the second inner gear 3 can be enlarged through fixed connection, so that the inner diameters and the outer diameters of the input shaft 6 and the eccentric wheel 1 can be enlarged, the inner holes of the whole transmission mechanism are increased, and the light weight of the structure is realized; in the prior art, the force points of the internal gear can be divided into three categories: between internal gear and the external gear, between internal gear and the output shaft, between internal gear and eccentric wheel 1, in this scheme, after two-stage internal gear fixed connection, first internal gear 2 and second internal gear 3 change with the atress condition between the eccentric wheel 1 respectively, first internal gear 2 and second internal gear 3 fixed connection, and with the surface sliding fit of eccentric wheel 1, first internal gear 2 and second internal gear 3 become the torsion between first internal gear 2 and second internal gear 3 with the power of eccentric wheel 1 respectively, make first internal gear 2 and second internal gear 3 respectively with first external gear 4 and the power between the second external gear 5 can transmit in the minizone, it all has great intensity to need not to require whole transmission structure, can realize the lightweight.
It should be noted that, the profile of the eccentric wheel 1 is a circular wheel, the first internal gear 2 and the second internal gear 3 can be matched with the eccentric wheel 1, so that the first internal gear 2 and the second internal gear 3 rotate along the axis of the eccentric wheel 1, that is, the outer side surface of the eccentric wheel 1 is matched with the inner side surfaces of the first internal gear 2 and the second internal gear 3, and the inner side surfaces of the first internal gear 2 and the second internal gear 3 can slide relatively along the outer side surface of the eccentric wheel 1, so that the first internal gear 2 and the second internal gear 3 perform a second circular motion along the axis of the eccentric wheel 1. Alternatively, the outer side surface of the eccentric wheel 1 may be an annular surface intersecting with the axis, or may be an annular surface parallel to the axis.
Specifically, referring to fig. 1 or fig. 6, the number of the eccentric wheels 6 may be 1, and the rotation of the eccentric wheels 6 is directly realized through the input shaft; the eccentric wheels can be multiple, the multiple eccentric wheels comprise multiple driving shafts, the multiple driving shafts are connected through connecting rods, and the multiple driving shafts are driven through one input shaft; through adopting a plurality of eccentric wheels 6 as the input, every eccentric wheel radius is littleer, is favorable to high-speed rotation, and a plurality of eccentric wheels have a plurality of drive shafts, shares pressure through a plurality of drive shafts, improves life.
It should be noted that, the input shaft 6 is fixedly connected with the eccentric wheel 1, the connection mode is not limited, including but not limited to integral molding, or connected through a connecting piece, and by fixedly connecting the input shaft 6 with the eccentric wheel 1, the stress condition between the internal gear and the output shaft and between the internal gear and the eccentric wheel 1 is changed, and the structural strength is further ensured.
It should be noted that, the eccentric wheel 1, the first internal gear 2 and the second internal gear 3 are in sliding fit, including but not limited to direct contact with each other, or are connected by a bearing.
In a specific embodiment, the number of times of the first internal gear 2 is M, the number of the first pins 41 is N, the number of times of the second internal gear 3 is P, the number of the second pins 52 is Q, and the reduction ratio X is calculated by the following formula: x is MQ/(MQ-NP); let the difference between the first ring gear 2 and the first pin gear 41 be U, that is, U-N-M, and the difference between the second ring gear 3 and the second pin gear 52 be V, that is, V-Q-P, and the reduction ratio X is calculated as: and X is MQ/(MV-UP).
In one embodiment, as shown in fig. 1-2, the first and second internal gears 2, 3 are cycloidal gears.
In the present embodiment, the first external gear 4 includes a plurality of first teeth 41, and the plurality of first teeth 41 mesh with the first internal gear 2; the second external gear 5 includes a pin gear 51 and a plurality of second pins 52, the pin gear 51 has a through hole for mounting the second pins 52, and the plurality of second pins 52 are engaged with the second internal gear 3.
In the present embodiment, the number of teeth of the first internal gear 2 is at least one less than the number of first teeth 41; the number of the second internal gear 3 is at least one less than the number of the second needle teeth 52.
In a specific solution of the present embodiment, the number of teeth of the first internal gear 2 is one less than the number of first teeth 41; the number of teeth of the second internal gear 3 is one less than that of the second needle teeth 52, i.e., U-N-M-1; V-Q-P-1; the reduction ratio X of the scheme is as follows: since X is MQ/(M-P), if the torque-to-weight ratio, the power-to-weight ratio, and the reduction ratio-to-weight ratio of the reduction gear need to be increased, the absolute value of M-P can be reduced to 1 as much as possible, and the optimum effect can be achieved.
In the scheme, the first inner gear 2 and the second inner gear 3 are both cycloidal gears, and the input shaft 6 drives the eccentric wheel 1 to realize the motion of the cycloidal gears. In the case where the reduction ratio is not required to be too large, specifically, when the reduction ratio is required to be within 80, it is more advantageous to use a cycloid wheel. The gear number of the cycloid wheel is too large, so that the pressure angle of the cycloid wheel is easily increased, the structural strength requirement is higher, the bearing pressure of the central shaft is too heavy and is easily damaged, and the torque bearing capacity of the whole equipment is obviously reduced.
In another embodiment, as shown in fig. 3 to 4, the first internal gear 2 and the second internal gear 3 are both involute gears.
In the present embodiment, the first external gear 4 and the second external gear 5 are both ring gears having internal teeth; the first internal gear 2 and the second internal gear 3 have external teeth that mesh with the first external gear 4 and the second external gear 5, respectively.
In the present embodiment, the number of teeth of the first internal gear 2 is at least two less than the number of teeth of the internal teeth of the first external gear 4; the number of teeth of the second internal gear 3 is at least two less than the number of teeth of the second external gear 5.
In a specific scheme of the embodiment, the number of teeth of the first internal gear 2 is less than that of the teeth of the first external gear 4 by 3; the number of teeth of the second internal gear 3 is 3 less than that of the second external gear 5, i.e. U-N-M-3; V-Q-P-3; the reduction ratio X of the scheme is as follows: since X is MQ/(3M-3P), a large shift reduction ratio can be obtained by changing MQ or M-P.
In this scheme, first internal gear 2 and second internal gear 3 are the involute gear, drive eccentric wheel 1 through input shaft 6 and realize the motion of involute gear, under the great condition of reduction ratio demand, adopt involute gear, involute gear has the advantage that the pressure angle is little, the bearing atress is little, the higher reduction ratio of realization that can relax.
In another embodiment, as shown in fig. 5, the driving device further includes a balance weight assembly 7 for eliminating eccentric vibration, the balance weight assembly 7 includes a connecting rod 71 and a balance weight 72, one end of the connecting rod 71 is connected to the balance weight 72, and the other end is connected to the input shaft 6, and by the arrangement of the balance weight assembly 7, the problem of eccentric vibration can be restrained, and the stability of the driving assembly can be improved.
Specifically, one or two of the weight assemblies 7 may be provided, and the weight assemblies 7 are disposed on surfaces of the first internal gear 2 and the second internal gear 3 away from each other.
Specifically, the axis of the input shaft 6 is located at a position intermediate between the axis of the eccentric wheel 1 and the balance weight 72
The above-mentioned embodiments are intended to illustrate the objects, technical solutions and advantages of the present invention in further detail, and it should be understood that the above-mentioned embodiments are merely exemplary embodiments of the present invention, and are not intended to limit the scope of the present invention, and any modifications, equivalent substitutions, improvements and the like made within the spirit and principle of the present invention should be included in the scope of the present invention.
Claims (8)
1. A differential gear transmission mechanism is characterized in that,
comprises an eccentric wheel (1), a first internal gear (2), a second internal gear (3), a first external gear (4), a second external gear (5) and an input shaft (6);
the first internal gear (2) and the second internal gear (3) are fixedly connected and coaxial;
the input shaft (6) is used for driving the eccentric wheel (1) to do eccentric motion; when the input shaft (6) drives the eccentric wheel (1) to move, the outer side surface of the eccentric wheel (1) is used for pushing the first internal gear (2) and the second internal gear (3) to do first circular motion along the axis of the input shaft (6);
the first internal gear (2) and the second internal gear (3) are in sliding fit with the outer side face of the eccentric wheel (1);
the first internal gear (2) is meshed with the first external gear (4);
the second internal gear (3) is meshed with the second external gear (5);
when the first internal gear (2) moves, the first external gear (4) is fixed and does not rotate; the first internal gear (2) is matched with the first external gear (4) to realize that the first internal gear (2) does second circular motion along the axis of the eccentric wheel;
the second external gear (5) can be driven to rotate by the second internal gear (3).
2. A differential gear mechanism according to claim 1, wherein the first (2) and second (3) internal gears are cycloidal gears; the first external gear (4) and the second external gear (5) are both pin gears; the first external gear (4) comprises a plurality of first needle teeth (41), and the first needle teeth (41) are meshed with the first internal gear (2); the second external gear (5) comprises a pin gear plate (51) and a plurality of second pin teeth (52), the pin gear plate (51) is provided with a through hole for mounting the second pin teeth (52), and the plurality of second pin teeth (52) are meshed with the second internal gear (3).
3. A differential gearing according to claim 2, characterized in that the number of teeth of the first internal gearwheel (2) is at least one less than the number of first needle teeth (41); the number of the second internal gear (3) is at least one less than that of the second needle teeth (52).
4. A differential gear mechanism according to claim 1, wherein the first (2) and second (3) internal gears are involute gears; the first external gear (4) and the second external gear (5) are both gear rings with internal teeth; the first internal gear (2) and the second internal gear (3) have external teeth that mesh with the first external gear (4) and the second external gear (5), respectively.
5. A differential gearing according to claim 4, characterized in that the number of teeth of the first internal gear (2) is at least two less than the number of teeth of the internal teeth of the first external gear (4); the number of teeth of the second internal gear (3) is at least two less than that of the teeth of the second external gear (5).
6. A differential gear mechanism according to any of claims 1-5, further comprising a balance block assembly (7) for eliminating eccentric vibrations, wherein the balance block assembly (7) comprises a connecting rod (71) and a balance weight (72), one end of the connecting rod (71) is connected with the balance weight (72), and the other end is connected with the input shaft (6).
7. A differential drive according to claim 1, characterized in that the input shaft (6) is fixedly connected to the eccentric (1).
8. A differential gear mechanism according to claim 1, characterized in that the eccentric (1) is connected to the first (2) and second (3) internal gear by means of bearings.
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| CN202110212127.XA CN113007285A (en) | 2021-02-25 | 2021-02-25 | Differential gear transmission mechanism |
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| CN202110212127.XA CN113007285A (en) | 2021-02-25 | 2021-02-25 | Differential gear transmission mechanism |
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| CN108843746A (en) * | 2018-08-15 | 2018-11-20 | 深圳市荣德机器人科技有限公司 | A kind of precision speed reduction device for robot |
| JP2020041680A (en) * | 2018-09-13 | 2020-03-19 | 株式会社ニッセイ | Differential decelerator |
| CN110005762A (en) * | 2019-04-17 | 2019-07-12 | 湖北汽车工业学院 | A kind of large transmission ratio planet-gear transmission device |
| CN111677819A (en) * | 2020-06-17 | 2020-09-18 | 祝宗煌 | Differential speed reducing mechanism and differential speed reducer |
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