TW201408909A - Gear transmission mechanism of transmission device - Google Patents

Abstract

This invention relates to a gear transmission mechanism of a transmission device, comprising: a first ring gear, a second ring gear, a primary planetary gear system, and a plurality of secondary planetary gear systems and a terminal planetary gear system arranged in such a way as to have central axes thereof disposed in parallel. The primary planetary gear system is provided with a first planetary gear and a first transmission gear coupled thereto, which are respectively engaged with a first sun gear and the secondary planetary gears in an axis-intersecting manner. The secondary planetary gear system is provided with a secondary planetary gear also engaged with a secondary sun gear in an axis-intersecting manner. The primary planetary gear system and the secondary and terminal planetary gear systems are coupled to each other via a plurality of coupling assemblies arranged therebetween, such that the rotation of the first planetary gear is transmitted to the adjacent secondary and terminal planetary gears, wherein the teeth of the first and second ring gears are arranged coaxially but are in inversely coaxial arrangement in respect to the teeth of the first, second and third sun gears which are coaxially arranged. The sun gears of each system can be selectively inhibited from rotating by a brake member so as to achieve the purpose of gear ratio change.

Description

Gear transmission of transmission

BACKGROUND OF THE INVENTION 1. Field of the Invention This invention relates to a gear shifting mechanism, and more particularly to a gear shifting mechanism for a transmission that utilizes a plurality of planetary gear systems.

Regarding the transmission of kinetic energy, the most common in industrial technology or everyday facilities is the use of gears. In addition to the increase and decrease of the input and output speed ratios, the gear transmission function is also often used on the input end which requires more work to reduce the force to be applied. In addition, the use of a bevel gear or the like to change the shaft angle of the conductive gear is also often used in power transmission applications requiring more degrees of freedom for work.

At present, the most common gear applications except the mechanical equipment, the most are the power transmission mechanism of the vehicle and the transmission. In particular, the automobile transmission gearbox with a relatively complicated structure utilizes the change of the gear ratio of the planetary gears to achieve the purpose of multi-speed shifting. However, these mechanisms must combine multiple sets of planetary gear systems, thereby making the whole mechanism large and complicated, and in manufacturing production. It costs a lot of money. In addition, in order to meet the needs of modern leisure, cycling has become one of the most popular ways. In order to enable the rider to overcome the resistance generated when going uphill, or to increase the speed of riding, the bicycle shifting system also A variety of gear shifting devices are available. The most common ones are flywheel combinations with different tooth diameters. With the front and rear gear ratios, the purpose of deceleration, twisting or acceleration is reduced.

When the flywheel tooth diameter is changed to achieve the purpose of shifting, in order to produce a multi-stage effect, it is often necessary to add more sprocket wheels on the front and rear sprocket wheels, thereby increasing the weight of the vehicle body and increasing the resistance of the actual ride. To this end, there is an improvement in the so-called internal transmission in the market, which is to set the transmission gear mechanism in the rear wheel hub to avoid The flywheel is contaminated with dust or impact, which affects the positioning of the chain and the lack of chaining. Although it is also reducing the volume of the gear mechanism, the planetary gear system utilized is also a conventional planar configuration. Referring to the first figure, a general planetary gear system 10 includes a ring gear 11, a sun gear 12 and a plurality of planet gears 13. The ring gear 11 is disposed coaxially with the sun gear 12, and the planetary gears 13 are meshed in an annular space between the ring gear 11 and the sun gear 12, and the planetary gears 13 are rotatably disposed on a planet. On the bracket 14, when the planetary gear 13 rotates, the planetary carrier 14 is simultaneously driven to rotate. The ring gear, the sun gear and the planetary gear can be fixed at one of them, and then one component inputs power and the other component outputs. Under normal circumstances, when the planetary bracket is used as the output end, regardless of whether the sun gear or the ring gear is used as the input end, a transmission ratio greater than 1 can be generated, and the purpose of the deceleration and twisting transmission is achieved. If the planetary bracket is used as the input end, whether the sun gear or the ring gear is used as the output end, the transmission ratio can be less than 1, and the purpose of accelerating the torque reduction transmission is achieved.

Therefore, with these transmissions, in order to achieve the purpose of multi-speed shifting, it is necessary to combine multiple sets of planetary gear systems, so that the transmissions can not only reduce the weight not much, but also the volume of the internal transmission due to the radial space requirement. There is no further reduction, so that these transmissions have the disadvantage of not being able to overcome the volume and weight reduction.

In addition, the sense of frustration during shifting often occurs between gears or between the sprocket wheels, which not only makes the shifting smooth, but also reduces the comfort of the rider when riding.

On the other hand, the shifting system using an array of planetary gears, which is limited to the rotation of the sun gear, usually clamps the rotation of the sun gear by a pin on the control shaft, since the card pin is a radial single The braking of the side often causes the sun gear to be off-axis after being used for a long time, thereby affecting the meshing close state between the gears, so that the durability of the gear is not good.

It is an object of the present invention to provide a special planetary gear system combination that achieves different tooth ratio setting effects by selective rotation of a plurality of sun gears.

A second object of the present invention is to provide a special planetary gear system combination method, which achieves a more multi-speed shifting effect by a combination of selective rotation of a plurality of sun gears and variations of wheel diameters of different pulleys.

A further object of the present invention is to provide a special planetary gear system combination method, which is different from the conventional planetary gear system mechanism, and the planetary gear shaft and the sun gear are arranged in a shaft to reduce the planetary gear system in the radial direction. The space required, in order to reduce the volume of the gear transmission of the overall transmission.

Another object of the present invention is to provide a special planetary gear system combination method, which can be applied to a relatively small transmission device or used in a transmission system of a vehicle by the effect of reducing the volume of the gear transmission of the overall transmission. On the one hand, it reduces the installation space, on the other hand, it can also achieve the purpose of weight reduction due to the volume reduction.

A further object of the present invention is to provide a special planetary gear system combination method, which utilizes a pulley and a belt transmission between a plurality of planetary gear systems, and the frustration caused by the gear meshing change during the buffer shifting by the flexible characteristics of the belt. Make the shift smoother.

Another object of the present invention is to provide a special planetary gear system combination method, which allows the rider to use the shifting system of the rickshaw by utilizing the flexible characteristics of the belt and the frustration caused by the gear meshing change during the buffer shifting. It does not feel the shifting during the shifting, which increases the ride comfort.

It is agglomeration of the present invention to provide a special planetary gear system set In combination with the annular brake member corresponding to the sun gear, the braking force of the sun gear is more evenly distributed, thereby maintaining the meshing state between the gears for a long time and prolonging the service life of the gear set.

In order to reduce the volume of the gear transmission of the transmission, extend the service life of the gear set, and provide shifting effects of different gear ratios while avoiding the frustration caused by shifting, the present invention provides a gear transmission mechanism for the transmission, including: a first ring gear, the first ring gear is rotatable about a central axis, and a first ring gear is axially protruded from the central axis; a first stage planetary gear system includes: a first sun gear, a first brake member, at least one first planetary gear, and at least one first transmission gear, wherein the first sun gear axially protrudes from the central axis to form a first external tooth, the first brake member is selectively The first sun gear is controlled to rotate, and each of the first planetary gears is coupled to each of the first transmission gears, and each of the first planetary gears is rotatable about a first planetary axis. The first planetary axis is perpendicular to the central axis such that the first planetary gear and the first transmission gear are respectively engageable with the first external tooth and the first ring tooth; a secondary planetary gear system, the secondary planetary gear systems and the first stage planetary gear system are juxtaposed along the central axis, each of the secondary planetary gear systems comprising: a primary gear, a second a brake member and at least one stage planetary gear, wherein the secondary sun gear axially protrudes from the central axis with a second external tooth, the second brake member selectively locking the secondary sun gear to control Rotating, each of the secondary planetary gears is rotatable about a second planetary axis, and the second planetary axis is perpendicular to the central axis such that the secondary planetary gears are engageable with the second external teeth; a second ring gear, the second ring gear is rotatable about the central axis, and a second ring tooth is axially protruded along the central axis; and a final planetary gear system, the final planetary gear system is along the center Axis The column is disposed at the axial ends of the secondary planetary gear systems, and includes: a final stage sun gear, a third brake member, at least one final stage planetary gear, and at least one second transmission gear, wherein the final stage sun gear A third external tooth is axially protruded from the central axis, and the third braking member selectively locks the final sun gear to control the rotation thereof, and each of the final planetary gears and each of the second transmission gears Connected and correspondingly disposed, each of the final stage planetary gears is rotatable about a third planetary axis, and the third planetary axis is perpendicular to the central axis, so that the final planetary gear and the second transmission gear are respectively The third external tooth and the second ring tooth are engaged; and a plurality of coupling assemblies, each of the coupling assemblies being respectively disposed in the first stage planetary gear system, the secondary planetary gear systems, and the Adjacent to the final stage planetary gear system, the coupling assemblies transmit the rotation of the first planetary gear to the secondary planetary gear of the adjacent secondary planetary gear system and the final stage planetary gear; wherein First ring tooth The second tooth coaxially arranged ring system, to which the former two coaxially arranged outer teeth of the first, the second and the third external tooth outer teeth disposed opposite axial line.

According to an embodiment of the present invention, the gear transmission mechanism of the transmission, wherein the first brake member, the second brake member and the third brake member are respectively sleeved on a control adjustment rod, wherein a first brake tooth is axially protruded from the central axis, and the first brake tooth is further displaceable by the first brake member and a first internal tooth is further disposed with the first sun gear Engaging the teeth to control the rotation of the first sun gear; each of the second brake members respectively axially protruding a second brake tooth along the central axis, each of the second brake teeth being responsive to each of the second brakes The member is selectively displaced to mesh with one of the second internal teeth of each of the secondary sun gears to control the rotation of each of the secondary sun gears; the third brake member is axially protruded according to the central axis a third brake tooth, wherein the third brake tooth can be selectively displaced by the third brake member to mesh with a third internal tooth of the final stage sun gear, and the final sun tooth is controlled The rotation of the wheel.

In addition, in the gear transmission mechanism of the transmission, each of the coupling assemblies may include: two pulleys and a belt, wherein the two pulley systems are coaxially coupled to the first planetary gear and the adjacent secondary planetary gears, respectively. Arranging, or respectively coaxially connected with two adjacent secondary planetary gears, or coaxially connected with the last secondary planetary gear and the adjacent secondary planetary gear, and can rotate synchronously, and the belt is Winding between two adjacent pulleys.

In another embodiment, the gear transmission of the transmission, the first stage planetary gear system can be further accommodated in a first bracket, and the secondary planetary gear systems are further respectively received in a second bracket The final planetary gear system is further disposed in a third bracket, wherein each of the sun gears is rotatably received in one of the receiving spaces of the corresponding brackets, and each of the The planetary gears are respectively rotatably fixed to the brackets by a bearing, and the brackets are coupled to each other and can be rotated together around the central axis by the rotation of the planetary gears.

According to the arrangement of the sun gear and the planetary gear shaft in the embodiment of the invention, and the tandem planetary gear system configuration mode, the disadvantage of increasing the volume generated by the shifting position can be overcome. At the same time, by the selective rotation combination of the sun gear in the embodiment of the present invention, more gear ratio changes can be generated, so that the shift position is greatly increased, and it is widely utilized for different shifting requirements. In addition, through the flexible cushioning of the belt, the present invention also avoids the frustration caused by the conventional shifting, makes the shifting smoother, and provides a more comfortable feeling for the rider when used in the rickshaw.

The embodiments of the present invention are further described in the following description, and the embodiments of the present invention are set forth to illustrate the present invention, and are not intended to limit the scope of the present invention. In the scope, when some changes and retouching can be made, the scope of protection of the present invention is attached to the patent application attached thereto. The scope is defined.

Please refer to FIG. 2 to FIG. 6 at the same time, which are respectively a schematic diagram of a combination diagram, an exploded view and a gear transmission mechanism of the embodiment of the present invention. A gear transmission mechanism of a transmission according to an embodiment of the present invention includes: a first ring gear 20, a first stage planetary gear system 30, a plurality of secondary planetary gear systems 40, a second ring gear 60 and a final planetary gear System 70. The first stage planetary gear system 30 and the plurality of secondary planetary gear systems 40 and the final stage planetary gear system 70 are juxtaposed with the central axis 201 as an axis.

The first ring gear 20 is rotatable about a central axis 201, and a first ring tooth 21 is axially protruded from the central axis 201. The first ring teeth 21 may be disposed in the axial direction at both ends, and the teeth may be in the form of an umbrella gear or a spur gear. The first ring gear 20 is provided with an external thread (not shown) on its outer circumferential surface for connection with other members as an input or output end of the power.

The first stage planetary gear system 30 includes a first sun gear 31, a first brake member 37, at least one first planet gear 32, and at least one first transmission gear 34. The first sun gear 31 is also pivoted about the central axis axis 201. A first outer tooth 311 and a first inner tooth 312 are axially protruded from the central axis 201. The tooth forms are It is an umbrella gear or a spur gear, but it is not limited to this. The first brake member 37 can be sleeved on a control adjustment rod 80, and a first brake tooth 371 is axially protruded from the central axis 201. The first brake tooth 371 can be selectively selected by the first brake member 37. The first inner tooth 312 provided by the first sun gear 31 is meshed to move, thereby controlling the rotation of the first sun gear 31.

The first planetary gears 32 are provided with at least one, preferably two or more, when When it is plural, it is better to set it in an equiangular distribution, so that its power transmission is more stable, the friction between teeth between gears is reduced, and the service life of the gear is prolonged. Each of the first planetary gears 32 is coupled to the first transmission gear 34 by a rotating shaft 33, and the two are rotated in conjunction. The first planetary gear 32 and the first transmission gear 34 rotate about the first planetary axis 301, and the first planetary axis 301 is perpendicular to the central axis 201, so that the first planetary gear 32 is coupled to the first sun gear. The first outer teeth 311 of the 31 are engaged, and the first transmission gear 34 meshes with the first ring teeth 21 of the first ring gear 20. However, the axial angle of the first planetary axis 301 and the central axis 201 is not limited thereto, and 60 degrees or 120 degrees is also an angle commonly used in applications, so that it is a preferred axis within 60 degrees to 120 degrees. Angle range. In conjunction with the change in the shaft angle, the first outer teeth 311 and the first planetary gears 32, and the first ring gear 21 and the first transmission gear 34 are meshed with any form of gear that can be engaged. The gears may be shaft intersecting gears, and the shaft angle may be between 60 degrees and 120 degrees, but not limited thereto, wherein 90 degrees is optimal. At this time, the gear form can be selected from a straight-toothed umbrella gear, and the volume of the embodiment of the present invention is further reduced by utilizing the characteristics of large rigidity and small volume. In addition, in order to further meet the requirements of low noise, high load and high speed, curved bevel gears can also be used, but not limited thereto.

The secondary planetary gear system 40 can be provided with only one or a plurality of, and when there are a plurality of gears, the tooth ratio change will be more abundant. A plurality of secondary planetary gear systems 40 or between the secondary planetary gear system 40 and the first stage planetary gear system 30 are juxtaposed along the central axis 201.

Each of the secondary planetary gear systems 40 includes a primary sun gear 41, a second brake 47, and at least a primary planetary gear 42. The secondary sun gear 41 is also pivoted about the central axis 201. A second outer tooth 411 and a second inner tooth 412 are axially protruded from the central axis 201. The tooth forms may be Bevel gear or spur gear, but not limited to this. The second brake member 47 can be sleeved on a control adjustment rod 80, and is axially protruded according to the central axis 201. There is a second brake tooth 471. The second brake tooth 471 can be selectively displaced by the second brake member 47 to mesh with the second internal tooth 412 provided by the secondary sun gear 41, thereby controlling the secondary sun. The rotation of the gear 41.

The secondary planetary gears 42 are provided with at least one, preferably two or more. When a plurality of the plurality of planetary gears 42 are provided, it is preferably arranged at an equiangular distribution, so that the power transmission is more stable, and the friction between the gear teeth is reduced and extended. Gear life. The secondary planetary gear 42 rotates about the secondary planetary axis 401, and the secondary planetary axis 401 is perpendicular to the central axis 201, such that the secondary planetary gear 42 is coupled to the second external tooth of the secondary sun gear 41. 411 is engaged. However, the axial angle of the secondary planetary gear 42 and the central axis 201 is not limited thereto, and 60 degrees or 120 degrees is also an angle commonly used in applications, so that it is a preferred axis within 60 degrees to 120 degrees. Angle range. In conjunction with the change in the shaft angle, the engaged second outer teeth 311 and the secondary planetary gears 42 are selected to be engageable in any form of gear. The gears may be shaft intersecting gears, and the shaft angle may be between 60 degrees and 120 degrees, but not limited thereto, wherein 90 degrees is optimal. At this time, the gear form can be selected from a straight-toothed bevel gear, and the volume of the embodiment of the present invention is further reduced by utilizing the characteristics of large rigidity and small volume. In addition, in order to further meet the requirements of low noise, high load and high speed, curved bevel gears can also be used, but not limited thereto.

A plurality of second ring gears 60 and a final stage planetary gear system 70 are juxtaposed in the axial ends of the secondary planetary gear systems 40. The second ring gear 60 is rotatable about a central axis 201, and a second ring gear 61 is axially protruded from the central axis 201. The second ring teeth 61 may be disposed in the axial direction, and the teeth may be in the form of an umbrella gear or a spur gear, but are not limited thereto. The second ring gear 70 can be provided with an external thread 62 on its outer circumferential surface for connection with other components as an input or output end of the power.

The final stage planetary gear system 70 includes: a final stage sun gear 71, a third brake member 77, at least one final stage planetary gear 72, and at least one second transmission tooth. Wheel 74. The final stage sun gear 71 is also rotated about the central axis axis 201. A third outer tooth 711 and a third inner tooth 712 are axially protruded from the central axis 201. The tooth forms are It is an umbrella gear or a spur gear, but it is not limited to this. The third brake member 77 can be sleeved on a control adjustment rod 80. A third brake tooth 771 is axially protruded from the central axis 201. The third brake tooth 771 can be selectively selected by the third brake member 77. The third internal tooth 712 provided in the final stage sun gear 71 is moved to mesh, thereby controlling the rotation of the final stage sun gear 71.

The final stage planetary gears 72 are provided with at least one, preferably two or more. When a plurality of planetary gears 72 are provided, it is preferably arranged in an equiangular distribution, so that the power transmission is more stable, and the friction between the gear teeth is reduced and extended. Gear life. Each of the final stage planetary gears 72 is coupled to the second transmission gear 74 by a rotating shaft 73, which are rotated in conjunction. The final stage planetary gear 72 and the second transmission gear 74 rotate about the final stage planetary axis 701, and the final stage planetary axis 701 is perpendicular to the central axis 201, so that the final stage planetary gear 72 is coupled with the final stage sun gear. The first outer teeth 711 of the meshing gears 71 are engaged, and the final stage gears 74 are meshed with the second ring teeth 61 of the second ring gears 60. However, the axial angles of the final planetary axis 701 and the central axis 201 are not limited thereto, and 60 degrees or 120 degrees is also an angle commonly used in applications, so that it is a preferred axis within 60 degrees to 120 degrees. Angle range. In conjunction with the change in the shaft angle, the meshing third external tooth 711 and the final planetary gear 72, and the second ring gear 21 and the second transmission gear 74 are selected to be engageable in any form of gear. The gears may be shaft intersecting gears, and the shaft angle may be between 60 degrees and 120 degrees, but not limited thereto, wherein 90 degrees is optimal. At this time, the gear form can be selected from a straight-toothed bevel gear, and the volume of the embodiment of the present invention is further reduced by utilizing the characteristics of large rigidity and small volume. In addition, in order to further meet the requirements of low noise, high load and high speed, curved bevel gears can also be used, but not limited thereto.

In the embodiment of the present invention, the first ring gear 21 and the second ring gear 61 are in the same axial direction. The first outer tooth 311, the second outer tooth 411 and the third outer tooth 711 are disposed in the opposite axial direction, so that the first ring gear 21 and the second ring are geared. The direction of rotation of the teeth 61 is exactly opposite to the rotation of the sun gears.

Between the first stage planetary gear system 30 and the adjacent secondary planetary gear system 40, and between the adjacent secondary planetary gear systems 40, and the secondary planetary gear system 40 and the final planetary gear system 70 The rotation of the first planetary gear 32 is transmitted to the secondary planetary gear 42 of the adjacent secondary planetary gear system 40 and then to the final planetary gear by a plurality of coupling assemblies 50. The final stage planetary gear 72 of system 70.

Each of the coupling assemblies 50 includes: two pulleys 51 and a belt 52, wherein the two pulleys 51 are coaxially connected to the first planetary gears 32 and the adjacent secondary planetary gears 42 by the rotating shafts 33 and 43, respectively, and Synchronous rotation; or coaxially connected to adjacent secondary planetary gears 42 by two rotating shafts 43 and synchronously rotating therewith; or rotating shafts 43 and 73 respectively with secondary planetary gears 42 and final planetary gears 72 coaxial phase connection, and can rotate synchronously; a belt 52 is respectively disposed between adjacent two pulleys 51.

In the embodiment of the present invention, the first stage planetary gear system 30 can be further disposed in a first bracket 35, and the second planetary gear systems 40 are respectively accommodated in a second bracket 44. The planetary gear system 70 is housed in a third bracket 75. The first sun gear 31, the secondary sun gear 41 and the final stage sun gear 71 are rotatably respectively accommodated in one of the accommodating spaces 351, 441 and 751 provided in the corresponding brackets, and the first planet The gear 32, the secondary planetary gears 42, and the final planetary gears 72 are rotatably fixed to the respective brackets in the mounting holes 352, 442, and 753 by bearings 36, 46, and 76, respectively. The first bracket 35 and the third bracket 75 are respectively provided with through grooves 353 and 754 for allowing the belt 52 to pass through.

The first bracket 35 and the third bracket 75 are respectively provided with a plurality of fixing holes 354 and 752, and the second brackets 44 are respectively provided with a plurality of slots 443. The brackets are connected by a plurality of fixing rods 45 corresponding to the grooves 443 and the fixing holes 354 and 752. The brackets are rotatable together about the central axis 201 by the rotation of the planetary gears.

Please refer to the fifth and sixth figures, which are related diagrams of the gear transmission mechanism in the embodiment of the present invention. The gear transmission mechanism of the transmission of the embodiment of the present invention can be used as the input end of the power by the first ring gear 20. When the first ring gear 20 rotates, the first transmission gear 34 meshing with the first ring gear 21 will rotate synchronously. The rotation of the first transmission gear 34 simultaneously drives the rotation of the coupled first planetary gear 32 and the pulley 51. When the first planetary gear 32 rotates, the first sun gear 31 that is meshed is further driven. At this time, in addition to the loss of friction or axial force, the input power does not vary with the idling of the first sun gear.

After the pulley 51 rotates, the rotation of the adjacent pulleys 51 is successively driven to further rotate the secondary sun gears 41 in the secondary planetary gear system 40. This last power is further transmitted by the second drive wheel 74 of the final stage planetary gear system 70 to the second ring gear 60. When the sun gear in each of the planetary gear systems is selectively restricted by the braking member, the planetary gears in the planetary gear system will rotate in the opposite direction in the axial direction, thereby driving the rotation of the bracket and the power of the input. The difference in transmission ratio is produced. Therefore, by combining the various sun gears to limit the rotation and the gear ratio setting by the embodiment of the present invention, a plurality of gear ratio combinations can be produced, and the utility model can be applied to various shifting systems. In addition, in the embodiment of the present invention, the first ring gear 21 and the second ring gear 61 are opposite to the first outer tooth 311, the second outer tooth 411, and the third outer tooth 711. When the gear is transmitted, the first ring gear 21 and the second ring gear 61 rotate in the opposite direction to the first sun gear 31, the secondary sun gear 41, and the final sun gear 71. Therefore, the change between the output and the input The design will also make the invention useful in reverse shifting systems.

On the other hand, in the embodiment of the present invention, the design of the input end of the first ring gear 20 is changed. The second ring gear 60 or the bracket is used as an input end or an output end, and the transmission mode is changed to apply to different applications. demand.

Please refer to the seventh figure, which is a schematic view of another embodiment of the present invention. In the embodiment of the present invention, the gear transmission mechanism of the transmission is also applied to the bicycle rear wheel hub, and the combination with the sprocket 90 and the clutch 91 causes the bicycle to generate a multi-stage shifting effect. A thread (not shown) may be further disposed on the clutch 91 as a fixed position of the power output or the input end.

10‧‧‧ planetary gear system

11‧‧‧ring gear

12‧‧‧Sun Gear

13‧‧‧ planetary gear

14‧‧‧ Planetary bracket

20‧‧‧First ring gear

201‧‧‧ center axis

21‧‧‧First ring tooth

30‧‧‧First stage planetary gear system

301‧‧‧First planetary axis

31‧‧‧First sun gear

311‧‧‧First external tooth

312‧‧‧First internal tooth

32‧‧‧First planetary gear

33‧‧‧ shaft

34‧‧‧First transmission gear

35‧‧‧First bracket

351‧‧‧ accommodating space

352‧‧‧Installation holes

353‧‧‧through slot

354‧‧‧Fixed holes

36‧‧‧ Bearing

37‧‧‧First brake

371‧‧‧First brake tooth

40‧‧‧Secondary planetary gear system

401‧‧‧second planetary axis

41‧‧‧Second sun gear

411‧‧‧Second external teeth

412‧‧‧Second internal tooth

42‧‧‧Secondary planetary gears

43‧‧‧ shaft

44‧‧‧second bracket

441‧‧‧ accommodating space

442‧‧‧Installation holes

443‧‧‧ Groove

45‧‧‧Fixed rod

46‧‧‧ bearing

47‧‧‧Second brake

471‧‧‧Second brake teeth

50‧‧‧ coupling assembly

51‧‧‧ Pulley

52‧‧‧Land

60‧‧‧second ring gear

61‧‧‧second ring teeth

62‧‧‧ external thread

70‧‧‧Last planetary gear system

701‧‧‧ Third planetary axis

71‧‧‧ final stage sun gear

711‧‧‧ Third external tooth

712‧‧‧The third internal tooth

72‧‧‧ final planetary gear

73‧‧‧ shaft

74‧‧‧Second transmission gear

75‧‧‧ third bracket

751‧‧‧ accommodating space

752‧‧‧Fixed holes

753‧‧‧Installation holes

754‧‧‧through slot

76‧‧‧ bearing

77‧‧‧3rd brake

771‧‧‧third brake teeth

80‧‧‧Control lever

90‧‧‧Sprocket

91‧‧‧Clutch

The first figure is a schematic diagram of a conventional planetary gear system.

The second drawing is a schematic view of an embodiment of the invention.

The third figure is an exploded perspective view of an embodiment of the present invention.

The fourth figure is another exploded perspective view of an embodiment of the present invention.

The fifth figure is a schematic view of a gear transmission mechanism in the embodiment of the present invention.

Figure 6 is a top plan view of the gear transmission mechanism in the embodiment of the present invention.

Figure 7 is a schematic view of another embodiment of the present invention.

20‧‧‧First ring gear

21‧‧‧First ring tooth

32‧‧‧First planetary gear

34‧‧‧First transmission gear

41‧‧‧Second sun gear

411‧‧‧Second external teeth

412‧‧‧First internal tooth

42‧‧‧Secondary planetary gears

47‧‧‧Second brake

471‧‧‧Second brake teeth

50‧‧‧ coupling assembly

51‧‧‧ Pulley

52‧‧‧Land

60‧‧‧second ring gear

61‧‧‧second ring teeth

62‧‧‧ external thread

71‧‧‧ final stage sun gear

72‧‧‧ final planetary gear

74‧‧‧Second transmission gear

77‧‧‧3rd brake

80‧‧‧Control lever

Claims (16)

A gear transmission mechanism for a transmission includes: a first ring gear, the first ring gear is rotatable about a central axis, and a first ring gear is axially protruded from the central axis; a first stage planetary gear system, The first sun gear, a first brake member, at least one first planetary gear, and at least one first transmission gear, wherein the first sun gear axially protrudes from the central axis to form a first external tooth The first braking member can selectively lock the first sun gear to control the rotation thereof, and each of the first planetary gears is coupled to each of the first transmission gears and correspondingly disposed, and each of the first planetary gears can be wound a first planetary axis is rotated, and the first planetary axis is perpendicular to the central axis such that the first planetary gear and the first transmission gear are respectively engageable with the first external tooth and the first ring tooth a plurality of secondary planetary gear systems, the secondary planetary gear systems and the first stage planetary gear system being juxtaposed along the central axis, each of the secondary planetary gear systems comprising: a primary sun a second brake member and at least a primary planetary gear, wherein the secondary sun gear axially protrudes from the central axis with a second external tooth, the second brake member selectively clamping the secondary The sun gear controls its rotation, and each of the secondary planetary gears is rotatable about a second planetary axis, and the second planetary axis is perpendicular to the central axis, so that the secondary planetary gear can be coupled to the second external tooth Engaging: a second ring gear, the second ring gear is rotatable about the central axis, and a second ring gear is axially protruded from the central axis; a final planetary gear system, the final planetary gear system Arbitrarily disposed along the central axis at the axial ends of the secondary planetary gear systems, including: a final stage sun gear, a third brake member, at least one final stage planetary gear, and at least a second transmission gear, wherein the final stage sun gear is axially convexly disposed with a third external tooth along the central axis, and the third brake member can selectively clamp the final stage sun gear to control the rotation thereof. The final stage planetary gears are coupled to the second transmission gear trains, and each of the final stage planetary gears is rotatable about a third planetary axis, and the third planetary axis is perpendicular to the central axis, so that the The final planetary gear and the second transmission gear are respectively engageable with the third external tooth and the second ring gear; and a plurality of coupling assemblies, each of the coupling assemblies being respectively disposed at the first stage Between the planetary gear system, the secondary planetary gear systems, and the final planetary gear system, the coupling assemblies can transmit the rotation of the first planetary gear to the adjacent secondary planetary gear system a stepped planetary gear and the final planetary gear; wherein the first ring tooth is disposed in the same axial direction as the second ring gear, and the first outer tooth and the second outer tooth are disposed in the same axial direction In the opposite axial direction with the third external tooth The gear transmission mechanism of the transmission of the first aspect of the invention, wherein the first brake member, the second brake member and the third brake member are respectively sleeved on a control adjustment rod, wherein the first a first brake tooth is axially protruded from the central axis, and the first brake tooth is further disposed with the first sun gear to be further disposed with the first sun gear. Engaging, controlling the rotation of the first sun gear; each of the second brake members respectively axially protruding a second brake tooth along the central axis, and each of the second brake teeth may be caused by each of the second brake members Selectively displaceing and engaging with one of the second internal teeth of each of the secondary sun gears to control the rotation of each of the secondary sun gears; the third brake member is axially convexly disposed along the central axis a third brake tooth, wherein the third brake tooth can be selectively displaced by the third brake member to mesh with a third internal tooth of the final stage sun gear The rotation of the final stage sun gear is made. The gear transmission mechanism of the transmission of claim 2, wherein the correspondingly engaged sun gear and the planetary gear are umbrella gears. The gear transmission mechanism of the transmission of claim 2, wherein the correspondingly engaged ring gears and transmission gears are umbrella gears. The gear transmission mechanism of the transmission of claim 2, wherein each of the coupling assemblies comprises: two pulleys and a belt, wherein the two pulley systems are coaxial with the first planetary gear and adjacent to the second The planetary gears are connected to each other, or are respectively coaxially connected with two adjacent planetary gears, or are respectively coaxially connected with the last secondary planetary gear and the adjacent secondary planetary gear, and can rotate synchronously with the same And the belt is wound between two adjacent pulleys. The gear transmission mechanism of the transmission of claim 5, wherein the correspondingly engaged sun gear and the planetary gear are shaft intersecting gears. The gear transmission mechanism of the transmission of claim 6, wherein a shaft angle between the correspondingly engaged sun gear and the planetary gear is 90 degrees. The gear transmission mechanism of the transmission of claim 6, wherein the correspondingly engaged sun gears and planetary gears are bevel gears. The gear transmission mechanism of the transmission of claim 8, wherein the correspondingly engaged sun gears and planetary gears are curved bevel gears. The gear transmission mechanism of the transmission of claim 1, wherein each of the coupling assemblies comprises: a second pulley and a belt, wherein the two pulleys are coaxial with the first planetary gear and adjacent to the second The planetary gears are connected to each other, or are respectively coaxially connected with two adjacent planetary gears, or respectively coaxial with the last secondary planetary gear and adjacent to the secondary planet The gears are connected to each other and can rotate synchronously, and the belt is wound between two adjacent pulleys. The gear transmission mechanism of the transmission of claim 10, wherein the correspondingly engaged sun gears and planetary gears are bevel gears. The gear transmission mechanism of the transmission of claim 1, wherein the first sun gear and the first planetary gear that are correspondingly engaged are umbrella gears. The gear transmission mechanism of the transmission of claim 1, wherein the first ring gear and the first transmission gear that are correspondingly engaged are umbrella gears. The gear transmission mechanism of the transmission of claim 1, wherein the first stage planetary gear system is further disposed in a first bracket, and the second planetary gear systems are further respectively received in a second bracket The final planetary gear system is further disposed in a third bracket, wherein each of the sun gears is rotatably received in one of the receiving spaces of the corresponding brackets, and each of the The planetary gears are respectively rotatably fixed to the brackets by a bearing, and the brackets are coupled to each other and can be rotated together around the central axis by the rotation of the planetary gears. The gear transmission mechanism of the transmission of claim 14, wherein the first bracket and the third bracket are respectively provided with a plurality of fixing holes, and the second brackets are respectively provided with a plurality of grooves, The brackets are connected by a plurality of fixing rods corresponding to the grooves and the fixing holes. The gear transmission mechanism of the transmission of claim 15, wherein the two ends of the fixing rod are respectively inserted into the fixing holes corresponding to the first bracket and the third bracket, The fixed rod is pressed into each The second brackets are disposed on the corresponding ones of the grooves, and the first brackets, the second brackets and the third brackets are respectively connected and fixed.