TWI718664B - Gear variable-speed mechanism - Google Patents

Abstract

A gear variable-speed mechanism used for providing at least two-stage transmission mechanism includes a transmission member, a first gear, a second gear, a third gear and a fourth gear. The transmission member includes a transmission disc, a first eccentric shaft and a second eccentric shaft. The first gear is eccentrically rotated by the first eccentric shaft. The second gear is eccentrically rotated by the second eccentric shaft. The first gear is rotated around the third gear for producing a planetary motion, thereby forming a first transmission mechanism. The second gear is rotated around the fourth gear for producing a planetary motion, thereby forming a second transmission mechanism. The transmission member, the first transmission mechanism and the second transmission mechanism are coupled with each other thereby generating a speed reducer or a speed increaser.

Description

Gear transmission mechanism

The present invention relates to a speed change mechanism, which can be used as a speed reducer or speed increaser; more particularly, the present invention relates to a gear speed change mechanism that adopts a pinwheel structure and can achieve multi-stage transmission.

Reducer is used to provide low speed and high torque, so it has been widely used in many occasions. For example, in the fields of wind power generation, lifting and transportation, precision machinery, industrial robots, machine tools, automation equipment, electric vehicles, mining and metallurgy, construction machinery, medical machinery, smart home, automobile manufacturing, shipbuilding and aviation industries, The application of reducer can be seen. The speed-increasing machine has fewer applications and can be mainly applied to power generation equipment.

Commonly used reducers include involute planetary gear reducers, harmonic reducers and cycloid reducers. However, the aforementioned reducer still has several disadvantages and limitations.

The limitation of the involute planetary gear reducer is that the adjustable range of the single-stage reduction ratio of this mechanism is limited, and it is not easy to miniaturize. With the higher requirements on the reduction ratio, one way is to achieve the single-stage involute planetary gear reducer in series (that is, to form a multi-stage transmission structure). The more the number of series connections, the more parts. The volume is relatively large and takes up space, which also increases the manufacturing cost. In addition, Involute gears have backlash problems, which will affect the performance and durability of the overall reducer.

The harmonic reducer is mainly composed of a flexible wheel and a rigid wheel. The limitation is that this mechanism is more prone to interference and other problems when the flexible wheel is deformed in the case of a low reduction ratio (for example: ≦17). Makes the operation not smooth. In the case of a high reduction ratio, the tooth profile becomes smaller due to the reduction of the gear module. When the reducer bears a large load, the flexspline is prone to damage due to its weaker strength, thereby reducing the service life of the reducer. . Therefore, this kind of harmonic reducer is only suitable for medium and low load occasions, and the adjustable range of its reduction ratio is also limited.

Cycloidal pinwheel reducers have many characteristics such as small size, high carrying capacity, long service life, large output torque, and high transmission efficiency, so they have been widely used. The structure of a conventional single-stage cycloidal pinwheel reducer roughly includes a pin wheel, a cycloidal wheel, an output pin, an eccentric shaft and an output shaft. The cycloidal wheel and the output shaft are connected by an output pin. When it is running, the pin wheel is fixed in the casing and does not move. When the input shaft rotates, the cycloidal wheel will revolve and rotate in the pin wheel to form planetary motion, so the cycloidal wheel can also be called the cycloidal planetary wheel. The output pin on the output shaft is sleeved on the ring hole on the cycloid planetary gear as output. Through the ring hole and the output pin fixed on the output shaft, the effect of reducing the speed and increasing the torque can be achieved. However, this single-stage cycloidal pinwheel reducer still has some shortcomings and limitations. The pin wheel and the cycloid wheel have a pin structure. In this way, although the spin of the needle pin can reduce the shear force brought by the cycloid wheel, the needle will be caused by collision and sliding contact. The pin wobbles slightly, resulting in less regular stress and speed fluctuations. In addition, as the reduction ratio increases, the increase in the number of pins will cause problems such as vibration and noise, and cycloid The gear teeth and needle diameter will be smaller and the strength will be reduced. Therefore, in addition to the limitation of the adjustable range of the reduction ratio, the manufacturing cost is also increased.

In the case of a low reduction ratio (≦17), due to the structure with a difference in the number of teeth, the gap between the pin and the pin is large, which easily leads to large fluctuations in stress and speed. Therefore, a cycloid with a small tooth difference is subsequently developed. Pin wheel reducer. The reduction ratio is determined by the difference in the number of teeth between the cycloidal wheel and the pin wheel. However, as the difference in the number of teeth increases, the tooth profile of the cycloidal gear will become sharper and the number of pins will increase, which will reduce the strength. The structure with three teeth difference will weaken the strength of the components, and the collision and sliding chances between components will be relatively increased, and the power transmission of the system will be relatively unstable. Therefore, the current market is still dominated by a structure with a difference of 2 teeth.

Recently, a cycloidal reducer without a pin wheel has also been proposed, which uses an internal tooth cycloidal wheel to replace the pin wheel with multiple pins (ie, non-pinwheel structure). Although this structure can improve the shortcomings of the traditional cycloid reducer, but as the speed ratio is higher, the number of teeth is bound to increase. However, in the case of limited space, if a large reduction ratio is to be achieved, a large number of teeth leads to a small tooth depth, which reduces the strength of the cycloid, so the strength of the reducer is limited. In addition, internal and external gears with multiple teeth are relatively difficult to manufacture and control precision, so the cost will increase.

In order to achieve high reduction ratio and high load capacity, the structure of the second-order reducer was born accordingly. Based on the structure of the second-order transmission, a kind of RV reducer has been developed. The RV reducer is composed of a first-stage involute planetary gear reduction mechanism and a second-stage cycloid pinwheel reduction mechanism in series. The operation method is that the input shaft of the sun gear rotates concentrically to transmit power to the planetary gears. The planetary gears and the first-stage internal gear make planetary revolutions. The first-stage output piece is connected to the planetary gear, and the first-stage output piece is connected to the planetary gear. The eccentric shaft is driven at the same time, the second-stage cycloidal wheel and the second-stage needle wheel The planetary motion is formed, and finally the power is transmitted to the second-stage output part, and then the second-stage output part outputs the power. A needle pin is provided between the second-stage cycloidal wheel and the second-stage pin wheel.

The above-mentioned RV reducer has relatively stable speed fluctuations and relatively good dynamic balance in structure, so it has better stress performance. However, its first-stage drive train uses an involute planetary gear reduction mechanism, and its tooth profile is involute. Therefore, if the backlash is too small, it may cause a risk of violent collisions between components, and it will also directly affect the speed of the reducer. Operational stability. However, the second-stage cycloidal wheel is used in the second-stage transmission system, and there will still be problems of movement error and stress fluctuation. When the load is large and running at high speed, the gear parts will be damaged, which will reduce the performance of the reducer. In addition, the manufacturing cost of the second-stage cycloidal wheel is relatively high.

At present, the existing cycloid reducer (whether it is a single-stage or two-stage design) is difficult to operate in reverse to become a speed increaser. Therefore, it is still necessary to develop a gear transmission mechanism that can be used as a reducer and a speed increaser, has high transmission performance, high load capacity, and can take into account manufacturing costs.

The present invention provides a gear transmission mechanism, which can form a transmission mechanism with two or more stages. As far as the second-stage transmission is concerned, it achieves high transmission performance and application ranges including low, medium and high-speed ratios through the first-stage transmission mechanism, transmission parts and second-stage transmission mechanism that are mutually coupled and linked.

In one embodiment of the present invention, a gear transmission mechanism is disclosed, which can be used to form a transmission mechanism with at least two stages or more. The gear transmission mechanism includes a transmission member, a first gear, a second gear, a third gear, and a fourth gear. The transmission component includes a body, a first eccentric shaft and a second eccentric shaft axis. The first eccentric shaft is arranged on one side of the main body. The second eccentric shaft is disposed on the other side of the body relative to the first eccentric shaft, wherein the first eccentric shaft and the second eccentric shaft have a phase difference. The first gear is driven by the first eccentric shaft to rotate eccentrically. The second gear is driven by the second eccentric shaft to rotate eccentrically. The third gear is coupled and linked with the first gear. The fourth gear is coupled and linked with the second gear. The first gear moves relative to the third gear planetary to form a first-stage transmission mechanism, and the first-stage transmission mechanism has a first-stage transmission ratio. The second gear relatively moves around the fourth gear planet to form a second-stage transmission mechanism, and the second-stage transmission mechanism has a second-stage transmission ratio. Through the coupling and linkage between the first-stage transmission mechanism, the transmission member and the second-stage transmission mechanism, the output function of deceleration or acceleration is achieved. A reduction ratio or an increase ratio of the gear transmission mechanism is obtained by comprehensively calculating the first-stage transmission ratio and the second-stage transmission ratio.

In the gear transmission mechanism of the above embodiment, the body of the transmission member may be in the shape of a disc.

In the gear transmission mechanism of the above embodiment, one eccentricity of the first eccentric shaft is the same or different from that of the second eccentric shaft.

In the gear transmission mechanism of the above embodiment, the difference between the number of teeth of the first gear and the number of teeth of the third gear is greater than or equal to one, and the difference between the number of teeth of the second gear and the number of teeth of the fourth gear is greater than or equal to one. And the difference between the number of teeth of the first gear and the number of teeth of the third gear is the same or different from the difference between the number of teeth of the second gear and the number of teeth of the fourth gear.

In the gear transmission mechanism of the above-mentioned embodiment, a plurality of bolts are respectively provided on the inner side of one of the first gear and one of the second gears, and a plurality of pin holes are provided on the body, and these pin holes are respectively provided for the bolts and the first gear of the first gear. This of two gears These plugs are inserted, and when a power is input by the first eccentric shaft and output by the fourth gear of the second-stage transmission mechanism, it forms a deceleration output and has a deceleration ratio.

In the gear transmission mechanism of the above embodiment, the central circle diameter of one of the pin holes of the body corresponding to the pins of the first gear is the same or different from that of the body corresponding to the pins of the second gear The diameter of the center circle of one of these pin holes.

In the gear transmission mechanism of the above embodiment, the reduction ratio can be expressed by the following relational expression: I=i2/(i2-i1); i1=n3/n1; and i2=n4/n2. Among them, I is the reduction ratio of the gear transmission mechanism, i1 is the first-stage transmission ratio, i2 is the second-stage transmission ratio, n1 is the number of teeth of the first gear, n2 is the number of teeth of the second gear, and n3 is the third gear One number of teeth, n4 is one number of teeth of the fourth gear. When the first-stage transmission ratio is less than the second-stage transmission ratio, the rotation direction of the power input is the same as the rotation direction of the power output; when the first-stage transmission ratio is greater than the second-stage transmission ratio, the rotation direction of the power input is the same as the power output The direction of rotation is opposite.

In the gear transmission mechanism of the above embodiment, the gear transmission mechanism further includes a fifth gear and a sixth gear. The outer side of one of the first gears and the outer side of one of the second gears are respectively provided with a plurality of pins. The inner side of one of the fifth gears and the inner side of one of the sixth gears are respectively provided with a plurality of pin holes for the plugs on the outer side of the first gear and the plugs on the outer side of the second gear to be inserted. When a power is input by the fifth gear and the sixth gear at the same time, the first gear and the second gear are driven respectively, and then output by the eccentric shaft, another speed-increasing output is formed and has another speed-increasing ratio. When one end of the shaft is input, and the fifth gear and the sixth gear are output at the same time, another reduction output is formed and has another reduction ratio.

In the gear transmission mechanism of the above embodiment, when the first-stage transmission ratio is equal to the second-stage transmission ratio, another increase ratio or another reduction ratio can be expressed by the following relationship: U=n1/(n3-n1)=n2 /(n4-n2), where U is another speed increase ratio or another reduction ratio, n1 is the number of teeth of the first gear, n2 is the number of teeth of the second gear, n3 is the number of teeth of the third gear, and n4 is the fourth gear The number of teeth.

In the gear transmission mechanism of the above embodiment, the number of transmission members, the first gear, the second gear, the third gear, and the fourth gear can be adjusted to form a multi-stage transmission mechanism with a transmission function of three or more stages. The multi-stage transmission mechanism includes an input end and at least one output end. One output power, one output speed and one output steering of the input end are the same or different from the one output power, one output speed and one output steering of the at least one output end.

300: Gear transmission mechanism

301: Shell

302: Third Gear

303: The first bearing

304: first gear

305: second bearing

311a: Bevel gear

312: Sixth Gear

312a: Bevel gear

320: transmission parts

400: Gear set

500: gear set

306: body

307: The third bearing

308: second gear

309: Fourth Gear

310: The fourth bearing

311: Fifth Gear

O, O1: pin hole

P, P1: latch

S1: The first eccentric shaft

S2: second eccentric shaft

D1: Diameter of the center circle of the ring hole

D2: Diameter of the center circle of the ring hole

Fig. 1 is an exploded view of the structure of the gear transmission mechanism according to an embodiment of the present invention; Fig. 2 is a schematic diagram showing the combination of the gear transmission mechanism of Fig. 1; Fig. 3 is an illustration of another embodiment according to the present invention Example of an exploded view of the structure of the gear transmission mechanism; Figure 4 is a schematic diagram showing the same diameter of the two ring holes of the gear transmission mechanism in Figure 3; Figure 5 is a diagram showing the second gear transmission mechanism in Figure 3 Schematic diagrams of the different diameters of the center circles of the ring holes; Fig. 6 is an exploded view of the structure of the gear transmission mechanism according to another embodiment of the present invention; Fig. 7 is a schematic diagram showing an application example of the gear transmission mechanism in Fig. 6; Fig. 8 is a diagram showing the structure of Fig. 6 A schematic diagram of another application example of the gear transmission mechanism; Fig. 9 shows the power output analysis diagram of the gear transmission mechanism in Fig. 3 as a reducer; Fig. 10 shows the components of the gear transmission mechanism in Fig. 3 The stress analysis diagram; Figure 11 shows the interval stress analysis diagram of the components in Figure 10; and Figure 12 shows the power output analysis diagram of the gear transmission mechanism in Figure 7 as a speed increaser or reducer .

In the following description, specific embodiments of the present invention will be described with reference to the accompanying drawings. Many practical details will be explained in the following description. However, these practical details should not be used to limit the present invention. That is, in some embodiments of the present invention, these practical details are unnecessary. In addition, for the sake of simplifying the drawings, some conventionally used structures and elements will be drawn in a simple schematic manner in the drawings; and repeated elements may be represented by the same numbers.

Please refer to Figure 1 and Figure 2. FIG. 1 is an exploded view of the structure of the gear transmission mechanism 300 according to an embodiment of the present invention. In this embodiment, the formation of a speed reducer is taken as an example, but it should be noted that the gear transmission mechanism 300 may also form a speed increaser. Figure 2 shows a schematic diagram of the combination of the gear transmission mechanism 300 in Figure 1 Figure. The gear transmission mechanism 300 includes a transmission member 320, a first gear 304, a second gear 308, a third gear 302 and a fourth gear 309. The transmission member 320 includes a body 306, a first eccentric shaft S1, and a second eccentric shaft S2. The first eccentric shaft S1 is disposed on one side of the main body 306. The second eccentric shaft S2 is disposed on the other side of the main body 306 relative to the first eccentric shaft S1. The first eccentric shaft S1 and the second eccentric shaft S2 have a phase difference. The phase difference can be 180 degrees or other angles.

In Fig. 1, the main body 306 of the transmission member 320 may be in the shape of a disc, and a plurality of pin holes O are opened thereon, and a plurality of bolts P are provided on the inner side of the first gear 304 and the inner side of the second gear 308 respectively. For example, when assembling, the number of pins P on the first gear 304 and the second gear 308 are both 8, so that they are symmetrically inserted into the pin holes O (the number is also 8) of the body 306 on both sides of the body 306, respectively. And the insertion depth is less than half of the thickness of the main body 306. The first gear 304 and the second gear 308 can be driven by the first eccentric shaft S1 and the second eccentric shaft S2, respectively.

The gear transmission mechanism 300 may further include a housing 301, a first bearing 303, a second bearing 305, a third bearing 307 and a fourth bearing 310. The shell 301 is used for accommodating components therein. The first bearing 303, the second bearing 305, the third bearing 307 and the fourth bearing 310 produce a supporting effect when the components produce relative movement (rotation or linear displacement). In other words, when the components move relative to each other on the shaft, the bearing can be used to maintain the center position of the shaft and control the stability of the movement of the components. Whether to use the bearing and the number of bearings used depends on different conditions. The embodiment shown in Figure 1 is only a bearing arrangement, and the present invention is not limited to its disclosure.

The gear transmission mechanism 300 of the present invention can form a multi-stage transmission structure, and can be used as a speed increaser or a reducer. For example, the embodiment in Figure 1 is The structure of the second-stage transmission, when used as a reducer, a power train is input by the first eccentric shaft S1, and the first gear 304 can be driven by the first eccentric shaft S1 to rotate eccentrically. At the same time, it also drives the second eccentric shaft on the other side. The eccentric shaft S2 rotates to drive the second gear 308 to rotate eccentrically. In Figure 1, the first gear 304 is an external gear, and the third gear 302 is an internal gear. The third gear 302 can accommodate the first gear 304 therein and is coupled with the first gear 304. Similarly, the second gear 308 is an external gear, and the fourth gear 309 is an internal gear. The fourth gear 309 can accommodate the second gear 308 therein, and the fourth gear 309 and the second gear 308 are coupled with each other. In other words, the first gear 304 can relatively move planetarily around the third gear 302 to form a first-stage transmission mechanism, and the first-stage transmission mechanism has a first-stage transmission ratio. The second gear 308 can relatively move planetarily around the fourth gear 309 to form a second-stage transmission mechanism, and the second-stage transmission mechanism has a second-stage transmission ratio. Through the first-stage transmission mechanism, the coupling and linkage between the transmission member 320 and the second-stage transmission mechanism, the fourth gear 309 finally achieves the purpose of output power and deceleration and torque increase. One of the reduction ratios of the reducer is obtained by comprehensively calculating the first-order transmission ratio and the second-order transmission ratio.

In the reducer of the above embodiment, the reduction ratio can be expressed by the following relational expression: I=i2/(i2-i1); i1=n3/n1; and i2=n4/n2. Where I is the reduction ratio of the reducer, i1 is the first gear ratio, i2 is the second gear ratio, n1 is the number of teeth of the first gear 304, n2 is the number of teeth of the second gear 308, and n3 is the third gear 302 is the number of teeth and n4 is the number of teeth of the fourth gear 309. The first-stage transmission ratio is not equal to the second-stage transmission ratio, and when the first-stage transmission ratio is less than the second-stage transmission ratio, the rotation direction of the first eccentric shaft S1 and the second eccentric shaft S2 and the rotation direction of the fourth gear 309 Same, that is, the direction of rotation of the input is the same as the direction of rotation of the output. When the first-stage transmission ratio is greater than the second-stage transmission ratio, the first deviation The rotation direction of the spindle S1 and the second eccentric shaft S2 is opposite to the rotation direction of the fourth gear 309, that is, the input rotation direction is opposite to the output rotation direction. In this way, the effect of changing the direction of rotation can be achieved by adjusting the first-stage transmission ratio and the second-stage transmission ratio, which can be applied to different applications.

Please refer to Figure 3, Figure 4 and Figure 5. FIG. 3 is an exploded view of the structure of a gear transmission mechanism 300 according to another embodiment of the present invention. FIG. 4 is a schematic diagram showing that the center circle diameters D1 and D2 of the two ring holes of the gear transmission mechanism 300 in FIG. 3 are equal. Fig. 5 is a schematic diagram showing the difference in the center circle diameters D1 and D2 of the two ring holes of the gear transmission mechanism 300 in Fig. 3. Similar to Fig. 1, the gear transmission mechanism 300 of the embodiment in Fig. 3 also forms a reducer. Most of the components of the gear transmission mechanism 300 in FIG. 3 are the same as those of the gear transmission mechanism 300 in the embodiment in FIG. 1, and will not be described separately. The main difference is that in Figure 3, the body 306 of the transmission member 320 can be provided with a plurality of pin holes O, and the inner side of the first gear 304 and the inner side of the second gear 308 are respectively provided with a plurality of pins P. When assembling, the number of pins P on the first gear 304 and the second gear 308 is 4, so that they are alternately inserted into the pin holes O (the number is 8) of the body 306 on the two sides of the body 306, and the number is inserted The depth is greater than half of the thickness of the main body 306 or the thickness of the main body 306. The pin hole O of the body 306 corresponding to the pin P of the first gear 304 has a central circle diameter D1 of the ring hole. The pin hole O of the body 306 corresponding to the pin P of the second gear 308 has a central circle diameter D2 of the ring hole. The center circle diameter D1 of the ring hole may be equal to the center circle diameter D2 of the ring hole (as shown in Fig. 4) or not equal to the center circle diameter D2 of the ring hole (as shown in Fig. 5). Similarly, the condition that the diameter D1 of the center circle of the ring hole is equal to or different from the diameter D2 of the center circle of the ring hole can also be applied to Fig. 1, and therefore has a wider applicability in the structure of the main body 306.

The gear transmission mechanism 300 of the present invention can be adapted to various conditions by adjusting the parameter values of various components. For example, suppose the first-order tooth number difference △t1=n3-n1; the second-order tooth number difference △t2=n4-n2, then the eccentricity of the first eccentric axis S1 c1=△t1*m1/2; the second eccentricity The eccentricity of the axis S2 is c2=△t2*m2/2, where m1 is the first-order gear module and m2 is the second-order gear module. The first-order tooth number difference Δt1 is the difference between the first gear 304's tooth number n1 and the third gear 302's tooth number n3, and the second-order tooth number difference Δt2 is the second gear 308's tooth number n2 and the fourth gear The difference between the number of teeth n4 of 309.

By changing the eccentricity c1 and the eccentricity c2, different stability and transmission effects can be obtained to meet different occasions. For example, when the eccentricity c1 and the eccentricity c2 are equal, if the first-order tooth number difference Δt1 is equal to the second-order tooth number difference Δt2, the first-order gear module m1 is equal to the second-order gear module m2; If the first-order tooth number difference Δt1 is not equal to the second-order tooth number difference Δt2, the first-order gear module m1 is different from the second-order gear module m2. Conversely, when the eccentricity c1 and the eccentricity c2 are different, if the first-order tooth number difference Δt1 is equal to the second-order tooth number difference Δt2, the first-order gear module m1 and the second-order gear module m2 can be different ; If the first-order tooth number difference Δt1 is not equal to the second-order tooth number difference Δt2, the first-order gear modulus m1 and the second-order gear modulus m2 can also be equal or different.

In the gear transmission mechanism 300 of the present invention, a pinwheel-less structure is adopted, so internal gears (ie, the third gear 302 and the fourth gear 309) are used to replace the conventional pinwheels. The gear transmission mechanism 300 of the present invention can also be applied to a situation with a higher number of teeth difference. That is, the difference between the number of teeth n1 of the first gear 304 and the number of teeth n3 of the third gear 302 (that is, the first-order tooth number difference Δt1) may be greater than or equal to one; the number of teeth n2 of the second gear 308 and the number of teeth of the fourth gear 309 The difference of n4 (that is, the number of teeth of the second order The difference Δt2) may be greater than or equal to one. The gear transmission mechanism 300 of the present invention can adopt a pin-wheel structure with at least one tooth difference or more. Through the transmission structure configuration of the present invention, not only can relatively low speed fluctuations and stress values be achieved, the stress fluctuations are also relatively regular. Compared with the structure using pin pins, the structure with no pin wheel and less tooth difference can not only reduce the fluctuation of the output speed, but also reduce the external gear (ie, the first gear 304, the second gear 308) and the internal gear. The stress fluctuations and stress values of important components such as gears (that is, the third gear 302, the fourth gear 309), and the stress distribution are also relatively even, which can greatly increase the service life of the overall mechanism and reduce the use cost.

In the gear transmission mechanism 300 of the embodiment in Figure 1 or Figure 3, the type of gear is an involute spur gear. In order to increase the stability and load-carrying capacity of the transmission system, the type of gear selected can be changed according to different conditions. change. Replace with. For example, the first gear 304 and the third gear 302 can be replaced with helical cylindrical gears or helical gears, but not limited to this. In the same way, the second gear 308 and the fourth gear 309 can also be replaced with helical cylindrical gears or helical gears, but not limited to this. In addition, in addition to the use of involute gears, the tooth profile of the gear adopts cycloidal gears and other tooth profile gears to meet the needs of different occasions.

The gear transmission mechanism 300 of the present invention can also be used as another mechanism for increasing speed and reducing speed. Please refer to Figure 6. FIG. 6 is an exploded view of the structure of a gear transmission mechanism 300 according to another embodiment of the present invention. The gear transmission mechanism 300 in Fig. 6 has most of the same components as the gear transmission mechanism 300 in Fig. 1 or Fig. 3. The main difference lies in the outside of the first gear 304 and the outside of the second gear 308 Each is provided with a plurality of bolts P1, and the fifth gear The inner side of the 311 and the sixth gear 312 are respectively provided with a plurality of pin holes O1 for inserting the pins P1 on the outer side of the first gear 304 and the outer side of the second gear 308 respectively. The first gear 304 is coupled and linked with the fifth gear 311 through the plug P1, and the second gear 308 is coupled and linked with the sixth gear 312 through the plug P1. The functions of the fifth bearing 313 and the sixth bearing 314 are as described in the previous embodiment, which are to produce support and motion stabilization effects. The housing 301 is used for accommodating components to form the gear transmission mechanism 300 in the embodiment shown in FIG. 6. The gear transmission mechanism 300 in the embodiment shown in Fig. 6 can be used as a speed increaser or a reducer. When used as a speed increaser, a power train is simultaneously input by the fifth gear 311 and the sixth gear 312 to drive the first gear 304 and the second gear 308 respectively. Through the coupling and linkage between the first-stage transmission mechanism, the transmission member 320 and the second-stage transmission mechanism, the first eccentric shaft S1 and the second eccentric shaft S2 are finally used to achieve the purpose of outputting power and increasing speed and torque. When used as a reducer, the power input and output directions are opposite, that is, a power is input from one end of the first eccentric shaft S1 and the second eccentric shaft S2, and power is output from the fifth gear 311 and the sixth gear 312 at the same time .

In the speed increaser (or reducer) of the above embodiment, the first-order transmission ratio is equal to the second-order transmission ratio, and the speed-increasing ratio or reduction ratio can be expressed by the following relationship: U=n1/(n3-n1)= n2/(n4-n2). Among them U is the speed increase ratio or reduction ratio. n1 is the number of teeth of the first gear 304, n2 is the number of teeth of the second gear 308, n3 is the number of teeth of the third gear 302, and n4 is the number of teeth of the fourth gear 309.

Please refer to Figure 7 and Figure 8 together. Fig. 7 is a schematic diagram showing an application example of Fig. 6. Fig. 8 is a schematic diagram showing another application example of the gear transmission mechanism 300 of Fig. 6. In Figure 7, the gear transmission mechanism 300 is used to form a speed increaser. The power source can be provided with a gear set 400 whose drive shaft is offset from the speed increaser. The spindles are parallel. Given a power to the transmission shaft of the gear set 400, the gear set 400 can simultaneously drive the fifth gear 311 and the sixth gear 312, and then the transmission mechanism of the present invention achieves the effect of increasing speed output. If the power input shaft and the output shaft are arranged vertically, please refer to Figure 8. The fifth gear 311 has to be replaced with a bevel gear 311a, and the sixth gear 312 should also be replaced with a bevel gear 312a. The power is input by one of the transmission shafts of the gear set 500, and the fifth gear 311 and the sixth gear 312 can be driven at the same time, and then the transmission mechanism of the present invention achieves the purpose of increasing speed output. If you want to use the mechanism in Figure 7 and Figure 8 above as a speed reducer, you just need to reverse the operation, so I won’t repeat it here.

In order to verify the feasibility of the present invention, the mechanisms in Figure 3 and Figure 7 are taken as examples to conduct dynamic analysis. Fig. 9 shows the power output analysis diagram of the gear transmission mechanism 300 in Fig. 3 as a reducer; Fig. 10 shows the stress analysis diagram of each component of the gear transmission mechanism 300 in Fig. 3; Fig. 11 It is a graph showing the interval stress analysis of the components in Fig. 10; Fig. 12 is a graph showing the power output analysis of the gear transmission mechanism 300 in Fig. 7 as a speed increaser or a reducer.

First, suppose that in the gear transmission mechanism 300 in FIG. 3, the number of teeth is given as: n1=60, n2=57, n3=63, and n4=60. After calculation, it is obtained that the reduction ratio is 400. Next, two situations such as c1=c2 and c1≠c2 are taken as examples to verify the feasibility of the present invention. Assuming that the gear modules of the first-stage transmission mechanism and the second-stage transmission mechanism are both 1.5mm, it is the condition of c1=c2. Assuming that the gear modules of the first-stage transmission mechanism and the second-stage transmission mechanism are 1.425mm and 1.5mm, respectively, it is a condition of c1≠c2. Suppose the input speed is set to 7200deg/sec (1200rpm) on the eccentric shaft, the input torque is 2N-m, and the output end is assumed to be no-load condition (idling), and the materials used for the parts are all alloy steel (Yield strength: 620MPa). Through the technology of dynamic analysis, the 9th figure after calculation shows the result of the output speed. Both eccentricity designs fluctuate up and down the theoretical value of 18deg/sec, and the average value of the speed is consistent with the theoretical value. This proves that the first The mechanism design shown in Figure 3 can get the correct output speed. Similarly, through the stress calculation technology, Figure 10 shows the stress of the first eccentric shaft S1 and the second eccentric shaft S2, the body 306, the first gear 304, the second gear 308, the third gear 302, and the fourth gear 309 Analyze the results. Figure 11 shows the stress situation below 2MPa, most of the component stresses fluctuate in this range. The results show that under the two eccentricity conditions, the stress is much smaller than the yield strength of the material. Therefore, it is confirmed that the mechanism design in Figure 3 does not involve unusual stress, so smooth operation can be obtained.

Similarly, suppose that in the gear transmission mechanism 300 of FIG. 7, the number of teeth is given as: n1=n2=60 and n3=n4=63. After calculation, the speed-increasing ratio or reduction ratio is 20. For example, when used as a speed-increasing machine, assuming that the input speed of the transmission shaft of the gear set 400 is 360deg/sec (60rpm), Figure 12 shows the first eccentric shaft S1 The rotation speed of the second eccentric shaft S2 and the second eccentric shaft S2 fluctuate up and down the theoretical value of 7200 deg/sec, and the average value of the rotation speed is consistent with the theoretical value. If it is used as a reducer, suppose an input speed of 7200deg/sec (1200rpm) is given on the first eccentric shaft S1 and the second eccentric shaft S2. Figure 12 shows that the rotational speed of the transmission shaft of the gear set 400 is at a theoretical value of 360deg/sec (60rpm) fluctuates up and down, and the average value of the speed is consistent with the theoretical value. The above proves that the mechanism in Figure 7 can also obtain the correct output speed. Since the mechanism in Figure 7 is similar to that in Figure 3, and the feasibility of the mechanism's transmission has been verified, the stress conditions of its components will not be repeated.

The gear transmission mechanism 300 disclosed in the present invention has the characteristics of high load-bearing capacity (small and uniform stress), large reduction ratio range, easy manufacturing, and compact structure (few parts, small size, and light weight). In addition, a speed reducer or speed increaser with higher rigidity, high transmission efficiency, low motion error and vibration noise can be developed. At the same time, it can also increase the service life of the overall mechanism and reduce the cost of use. In addition, the first-stage and second-stage systems referred to in the present invention take the second-stage transmission as an example, but are not limited thereto. In different situations, different numbers of transmission members 320 and components similar to the first-level transmission mechanism or the second-level transmission mechanism can also be used to form a multi-level transmission mechanism through the coupling and linkage of the transmission member 320 and multiple gears ( For example, three-stage, four-stage, etc.), so that the output power, output speed and output rotation of one input end and one output end of the multi-stage transmission mechanism are the same or different, so as to achieve different acceleration or deceleration effects.

Although the present invention has been disclosed in the above embodiments, it is not intended to limit the present invention. Therefore, the scope of protection of the present invention shall be subject to the scope of the attached patent application.

300‧‧‧Gear transmission mechanism

301‧‧‧Shell

302‧‧‧The third gear

303‧‧‧First bearing

304‧‧‧The first gear

305‧‧‧Second Bearing

306‧‧‧Ontology

307‧‧‧Third bearing

308‧‧‧Second gear

309‧‧‧Fourth gear

310‧‧‧Fourth bearing

320‧‧‧Transmission parts

O‧‧‧Pin hole

P‧‧‧Latch

S1‧‧‧The first eccentric shaft

S2‧‧‧Second eccentric shaft

Claims (10)

A gear transmission mechanism, which is used to form a transmission mechanism with at least two steps or more, comprises: a transmission member, the transmission member including: a body; a first eccentric shaft arranged on one side of the body; and a second eccentric A shaft is arranged on the other side of the body relative to the first eccentric shaft, wherein the first eccentric shaft and the second eccentric shaft have a phase difference; a first gear, which is driven by the first eccentric shaft to rotate eccentrically A second gear, which is driven by the second eccentric shaft to rotate eccentrically; a third gear, which is coupled and linked with the first gear; and a fourth gear, which is coupled and linked with the second gear; wherein, the The first gear moves relatively around the third gear planet to form a first-stage transmission mechanism, the first-stage transmission mechanism has a first-stage transmission ratio, and the second gear relatively moves around the fourth gear planet to form a first-stage transmission mechanism. A second-stage transmission mechanism, the second-stage transmission mechanism has a second-stage transmission ratio, and through the first-stage transmission mechanism, the transmission member and the second-stage transmission mechanism are mutually coupled and linked to form a deceleration output or a speed increase output And a reduction ratio or an increase ratio of the gear transmission mechanism is obtained by comprehensively calculating the first-stage transmission ratio and the second-stage transmission ratio. According to the gear transmission mechanism described in item 1 of the scope of patent application, the body of the transmission member is in the shape of a disc. The gear transmission mechanism described in item 1 of the scope of patent application, wherein an eccentricity of the first eccentric shaft is the same or different from an eccentricity of the second eccentric shaft. As described in the first item of the scope of patent application, the difference between the number of teeth of the first gear and the number of teeth of the third gear is greater than or equal to one, and the number of teeth of the second gear is greater than or equal to one of the number of teeth of the fourth gear. A difference between a number of teeth is greater than or equal to one, and the difference between the number of teeth of the first gear and the number of teeth of the third gear is the same or different from the number of teeth of the second gear and the number of teeth of the fourth gear The difference in the number of teeth. The gear transmission mechanism described in item 1 of the scope of patent application, wherein a plurality of bolts are respectively provided on the inner side of one of the first gear and the inner side of one of the second gears, and the body is provided with a plurality of pin holes, and the pin holes are respectively provided with The plug pins of the first gear and the plug pins of the second gear are inserted, and when a power is input by the first eccentric shaft and output by the fourth gear of the second-stage transmission mechanism, the deceleration is formed Output and have this reduction ratio. The gear transmission mechanism described in item 5 of the scope of patent application, wherein the center circle diameter of one of the pin holes of the body corresponding to the pins of the first gear is the same as or different from that of the second gear The diameter of the center circle of one of the pin holes of the body corresponding to the plug pins. For the gear transmission mechanism described in item 5 of the scope of patent application, the reduction ratio is expressed by the following relational expression: I=i2/(i2-i1); i1=n3/n1; and i2=n4/n2; where I Is the reduction ratio of the gear transmission mechanism, i1 is the first-stage transmission ratio, i2 is the second-stage transmission ratio, n1 is the number of teeth of the first gear, n2 is the number of teeth of the second gear, and n3 is The number of teeth of the third gear, n4 is the number of teeth of the fourth gear; wherein when the first-stage transmission ratio is less than the second-stage transmission ratio, the rotation direction of the power input is the same as the rotation direction of the power output; When the first-stage transmission ratio is greater than the second-stage transmission ratio, the rotation direction of the power input is opposite to the rotation direction of the power output. According to the gear transmission mechanism described in item 1 of the scope of patent application, the gear transmission mechanism further includes a fifth gear and a sixth gear, and an outer side of the first gear and an outer side of the second gear are respectively provided with a plurality of Latch, one of the fifth gears and one of the sixth gears are respectively provided with a complex Pin holes for inserting the pins on the outer side of the first gear and the pins on the outer side of the second gear respectively. When a power is input from the fifth gear and the sixth gear at the same time, respectively When the first gear and the second gear are driven, and then output by the eccentric shaft, another speed-increasing output is formed with another speed-increasing ratio. When the power is input from one end of the eccentric shaft, the fifth gear and the When the sixth gear is output at the same time, it forms another reduction output and has another reduction ratio. For the gear transmission mechanism described in item 8 of the scope of patent application, when the first-stage transmission ratio is equal to the second-stage transmission ratio, the other increase ratio or the other reduction ratio is expressed by the following relationship: U=n1/(n3-n1)=n2/(n4-n2), where U is the other increase ratio or the other reduction ratio, n1 is the number of teeth of the first gear, n2 is the second gear The number of teeth, n3 is the number of teeth of the third gear, and n4 is the number of teeth of the fourth gear. The gear transmission mechanism described in item 1 of the scope of patent application, wherein the number of the transmission member, the first gear, the second gear, the third gear, and the fourth gear are adjusted to form a transmission function with three or more stages A multi-stage transmission mechanism. The multi-stage transmission mechanism includes an input end and at least one output end. One of the input ends has an output power, an output speed, and an output steering. The at least one output end has an output power, an output Rotation speed and an output direction of rotation are the same or different.

Images