CN206175581U - Many grades of variable transmission mechanism of coaxial line planet transmission - Google Patents
Many grades of variable transmission mechanism of coaxial line planet transmission Download PDFInfo
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Abstract
本实用新型公开了一种同轴线行星传动多档变速传动机构，它具有一个输入端，一个输出端，它包括输入轴、离合器、制动器、输出轴以及由太阳轮、行星轮、行星架、齿圈组成的行星传动机构，离合器为多个，对应多个档位，每档离合器与单独的行星传动机构连接，多个行星传动机构的太阳轮、输入轴、输出轴设置在同一轴线上，输入轴通过离合器与不同档位行星传动机构的一级太阳轮连接，每个行星传动机构的一级太阳轮上连接有制动器Ⅰ，行星传动机构的末级行星架通过末级行星轮与齿圈连接，末级行星架连接有制动器Ⅱ，齿圈与输出轴连接，该机构不仅能够实现同轴线行星传动的多档变速，而且能够实现不同档位传动比相差悬殊的不同传动，且随动齿轮转速不会过高而影响到正常行驶。
The utility model discloses a coaxial planetary transmission multi-speed transmission mechanism, which has an input end and an output end, which includes an input shaft, a clutch, a brake, an output shaft and a sun gear, a planetary gear, a planet carrier, The planetary transmission mechanism composed of the ring gear has multiple clutches corresponding to multiple gear positions. Each clutch is connected to a separate planetary transmission mechanism. The sun gears, input shafts, and output shafts of multiple planetary transmission mechanisms are arranged on the same axis. The input shaft is connected to the first-stage sun gear of the planetary transmission mechanism with different gears through the clutch. The first-stage sun gear of each planetary transmission mechanism is connected to the brake I. The final planetary carrier of the planetary transmission mechanism passes through the final-stage planetary gear and the ring gear. connection, the final planetary carrier is connected with the brake II, and the ring gear is connected with the output shaft. This mechanism can not only realize the multi-speed transmission of the coaxial planetary transmission, but also realize different transmissions with different transmission ratios of different gears, and follow-up The gear speed will not be too high to affect normal driving.
Description
技术领域technical field
本实用新型涉及减速器领域，具体讲是一种同轴线行星传动多档变速传动机构。The utility model relates to the field of reducers, in particular to a coaxial planetary transmission multi-speed variable transmission mechanism.
背景技术Background technique
行星传动被广泛应用于很多领域，目前，市场上尚未出现同轴线的多级行星传动机构，而且要实现行星机构的换挡，特别是多档、大传动比的减速机换挡，又不影响正常行驶的变档传动机构。Planetary transmission is widely used in many fields. At present, there is no coaxial multi-stage planetary transmission mechanism on the market, and it is necessary to realize the gear shifting of the planetary mechanism, especially the gear shifting of the multi-speed and large transmission ratio reducer. A gear shifting mechanism that affects normal driving.
发明内容Contents of the invention
本实用新型的目的在于解决上述技术问题，提供一种同轴线行星传动多档变速传动机构，该机构不仅能够实现同轴线行星传动的多档变速，而且能够实现不同档位传动比相差悬殊的不同传动，且随动齿轮转速不会过高而影响到正常行驶。The purpose of this utility model is to solve the above-mentioned technical problems, and to provide a multi-speed transmission mechanism of coaxial planetary transmission, which can not only realize multi-speed transmission of coaxial planetary transmission, but also realize different transmission ratios of different gears. Different transmissions, and the speed of the driven gear will not be too high to affect normal driving.
为实现上述实用新型目的，本实用新型所采取的技术方案为：For realizing above-mentioned utility model purpose, the technical scheme that the utility model takes is:
一种同轴线行星传动多档变速传动机构，它具有一个输入端，一个输出端，它包括输入轴、离合器、制动器、输出轴以及由太阳轮、行星轮、行星架、齿圈组成的行星传动机构，离合器为多个，对应多个档位，每档离合器与单独的行星传动机构连接，多个行星传动机构的太阳轮、输入轴、输出轴设置在同一轴线上，输入轴通过离合器与不同档位行星传动机构的一级太阳轮连接，每个行星传动机构的一级太阳轮上连接有制动器Ⅰ，行星传动机构的末级行星架通过末级行星轮与齿圈连接，末级行星架连接有制动器Ⅱ，齿圈与输出轴连接。A coaxial planetary transmission multi-speed transmission mechanism, which has an input end and an output end, which includes an input shaft, a clutch, a brake, an output shaft, and a planet composed of a sun gear, a planetary gear, a planet carrier, and a ring gear. In the transmission mechanism, there are multiple clutches corresponding to multiple gear positions. Each clutch is connected to a separate planetary transmission mechanism. The sun gears, input shafts, and output shafts of multiple planetary transmission mechanisms are arranged on the same axis. The first-stage sun gears of the planetary transmission mechanism with different gears are connected. The first-stage sun gear of each planetary transmission mechanism is connected with the brake I. The final planetary carrier of the planetary transmission mechanism is connected with the ring gear through the final planetary gear. The frame is connected with brake II, and the ring gear is connected with the output shaft.
所述的行星传动机构为一级行星传动或者是二级封闭式行星传动或者是多级封闭式行星传动，如各个档位离合器对应连接同级的行星传动或者是不同级的行星传动的组合形式。The planetary transmission mechanism is a one-stage planetary transmission or a two-stage closed planetary transmission or a multi-stage closed planetary transmission. For example, each gear clutch is connected to a planetary transmission of the same level or a combination of planetary transmissions of different levels. .
当某档位离合器与一级行星传动构连接时，一级行星架即为末级行星架，输入轴与该档位离合器连接，该档位离合器与一级太阳轮连接，一级太阳轮与行星轮啮合连接，行星轮设置在末级行星架上并与之连接，末级行星架与齿圈啮合连接，末级行星架与制动器Ⅱ连接，齿圈与输出轴连接。When a gear clutch is connected to the first-stage planetary transmission mechanism, the first-stage planetary carrier is the last-stage planetary carrier, the input shaft is connected to the gear clutch, the gear clutch is connected to the first-stage sun gear, and the first-stage sun gear is connected to the first-stage sun gear. The planetary gears are meshed and connected, the planetary gears are arranged on the final planet carrier and connected with it, the final planet carrier is meshed and connected with the ring gear, the final planet carrier is connected with the brake II, and the ring gear is connected with the output shaft.
当某档位与二级封闭式行星传动机构连接时，输入轴与该档位离合器连接，该档位离合器与一级太阳轮连接，一级太阳轮连接有制动器Ⅰ，一级太阳轮与一级行星轮啮合，一级行星轮与一级齿圈啮合，一级行星轮与一级行星架连接，一级行星架与二级太阳轮连接，二级太阳轮与二级行星轮啮合，二级行星轮与二级齿圈啮合，二级行星轮与二级行星架连接，二级行星架与制动器Ⅱ连接，此时二级行星架即为末级行星架；When a certain gear is connected to the secondary closed planetary transmission mechanism, the input shaft is connected to the gear clutch, the gear clutch is connected to the first-stage sun gear, the first-stage sun gear is connected to the brake I, and the first-stage sun gear is connected to the first-stage sun gear. The first-stage planetary gear is meshed, the first-stage planetary gear is meshed with the first-stage ring gear, the first-stage planetary gear is connected with the first-stage planet carrier, the first-stage planet carrier is connected with the second-stage sun gear, the second-stage sun gear is meshed with the second-stage planetary gear, The first-stage planetary gear meshes with the second-stage ring gear, the second-stage planetary gear is connected with the second-stage planetary carrier, and the second-stage planetary carrier is connected with the brake II. At this time, the second-stage planetary carrier is the last-stage planetary carrier;
当某档位与N级封闭式行星传动机构连接时，输入轴与该档位离合器连接，该档位离合器与一级太阳轮连接，一级太阳轮连接制动器Ⅰ，一级太阳轮与一级行星轮啮合，一级行星轮与一级齿圈啮合，一级行星轮与一级行星架连接，一级行星架与下一级太阳轮连接，直到N-1级行星架与N级太阳轮连接，N级太阳轮与N级行星轮啮合，N级行星轮与N级齿圈啮合，N级行星轮与末级行星架连接，末级行星架连接制动器Ⅱ。When a gear is connected to the N-stage closed planetary transmission mechanism, the input shaft is connected to the gear clutch, the gear clutch is connected to the first-stage sun gear, the first-stage sun gear is connected to the brake I, and the first-stage sun gear is connected to the first-stage sun gear. The planetary gear meshes, the first-level planetary gear meshes with the first-level ring gear, the first-level planetary gear is connected with the first-level planet carrier, the first-level planet carrier is connected with the next-level sun gear, until the N-1 level planet carrier is connected with the N-level sun gear Connection, the N-level sun gear meshes with the N-level planetary gear, the N-level planetary gear meshes with the N-level ring gear, the N-level planetary gear is connected with the final planet carrier, and the final planet carrier is connected with the brake II.
所述的每一档位对应的离合器与单独的行星传动机构连接，每一个行星传动机构的一级太阳轮处设置有制动器Ⅰ，末级行星架处设置有制动器Ⅱ。The clutch corresponding to each gear is connected to a separate planetary transmission mechanism. The first-stage sun gear of each planetary transmission mechanism is provided with a brake I, and the last-stage planet carrier is provided with a brake II.
各个行星传动机构的太阳轮为同轴线套装，彼此不影响转动。The sun gears of each planetary transmission mechanism are coaxial sets, which do not affect each other's rotation.
所有档位的齿圈一体式连接。The ring gears of all gears are connected in one piece.
所述制动器Ⅰ和制动器Ⅱ的操纵方式为M-机动、H-液动、P-气动、E-电动之中任一一种或两种组合形式。The operation mode of the brake I and the brake II is any one of M-motor, H-hydraulic, P-pneumatic, E-electric, or a combination of both.
所述离合器的类型是啮合式离合器或摩擦式离合器或电磁式离合器或离心摩擦离合器，离合器的操纵方式可以是：M-机动、H-液动、P-气动、E-电动之中任一一种或多种组合形式。The type of clutch is meshing clutch or friction clutch or electromagnetic clutch or centrifugal friction clutch, and the operation mode of the clutch can be any of: M-motor, H-hydraulic, P-pneumatic, E-electric one or more combinations.
本实用新型的工作原理为：The working principle of the utility model is:
每个档位通过输入端制动器Ⅰ与末级行星架制动器Ⅱ协同工作，使各档行星机构工作在主动状态或处于低速随动状态：输入端制动器打开，末级行星架闭合，该档处于主动状态；输入端制动器闭合，末级行星架打开，该档处于低速随动状态。Each gear position cooperates with the final planetary carrier brake II through the input end brake Ⅰ, so that the planetary mechanism of each gear works in the active state or in the low-speed follow-up state: the input end brake is opened, the final stage planetary carrier is closed, and the gear is in the active state. State: the brake at the input end is closed, the planetary carrier of the final stage is opened, and this gear is in the low-speed follow-up state.
所有档位离合器打开，当某一个档位的输入端制动器打开，其余档位输入端制动器闭合，该档位末级行星架制动器闭合，其余档位末级行星架制动器打开，该档位离合器闭合，该档位行星机构工作，其余档位行星机构进入低速随动状态，该换挡机构输出一种转速；第二个档位需要工作时，当前工作档位的离合器打开，当前工作档位的输入端制动器闭合，当前工作档位的末级行星架制动器打开，第二个档位的输入端制动器打开，第二个档位的末级行星架制动器闭合，第二个档位的离合器闭合，第二个档位行星机构工作，其余档位行星机构进入低速随动状态，该换挡机构输出另一种转速；以此类推。All gear clutches are open, when the input end brake of a certain gear is opened, and the other gear input end brakes are closed, the last stage planetary carrier brake of this gear is closed, and the final stage planetary carrier brake of other gears is opened, and the gear clutch is closed , the planetary mechanism of this gear is working, and the planetary mechanism of other gears enters the low-speed follow-up state, and the shifting mechanism outputs a speed; when the second gear needs to work, the clutch of the current working gear is opened, and the clutch of the current working gear The brake at the input end is closed, the brake of the final planetary carrier of the current working gear is opened, the brake of the input end of the second gear is opened, the brake of the final planetary carrier of the second gear is closed, the clutch of the second gear is closed, The second gear planetary mechanism works, and the rest of the gear planetary mechanisms enter the low-speed follow-up state, and the shifting mechanism outputs another speed; and so on.
当各档减速比相差不是特别大，任意一个档位输入，其余的档位随动，所有随动档转动部件均不超过其允许转速时，所有档位的输入端制动器与末级行星架制动器可以不安装。When the reduction ratio of each gear is not particularly large, any gear is input, the rest of the gears follow, and all the rotating parts of the follower gears do not exceed their allowable speeds, the input end brakes of all gears and the final planetary carrier brake You can not install it.
也可以根据各档的随动转速有选择的进行安装制动器，即：需要安装制动器的档位就安装上制动器，不需要安装制动器的档位不安装。It is also possible to selectively install the brakes according to the follow-up speed of each gear, that is, the gears that need to be installed with the brakes are installed with the brakes, and the gears that do not need to be installed with the brakes are not installed.
在各档输入端安装输入端制动器，同时在各档末级行星架上安装制动器，解决了随动齿轮转速太高的问题。如：第一档的传动比为3，第二档的传动比为：i=134-1=28560或更大，当第一档主动时，虽然第二档的传动比很大，但第二档仍然能够低速随动！需要某一个档位的传动比变得更大，只要增加该档行星减速的级数即可，增加级数后换挡机构的径向尺寸不用加大，其轴向尺寸是各级行星机构轴向尺寸的叠加。The input end brake is installed on the input end of each gear, and the brake is installed on the last stage planet carrier of each gear, which solves the problem of too high speed of the driven gear. For example: the transmission ratio of the first gear is 3, the transmission ratio of the second gear is: i=13 4 -1=28560 or more, when the first gear is active, although the transmission ratio of the second gear is very large, the second gear The second gear can still move at low speed! It is necessary to increase the transmission ratio of a certain gear, just increase the number of planetary reduction stages of this gear, and the radial dimension of the shifting mechanism does not need to be increased after increasing the number of stages, and its axial dimension is the axis of the planetary mechanism at each level Overlay to dimensions.
本实用新型的有益效果为：The beneficial effects of the utility model are:
提供一种同轴线行星传动多档变速传动机构，该机构能够实现同轴线行星传动的多档变速，且空闲档的行星机构处于低速随动状态；每一档传动比的实现范围变得更大，例如：当该档由五级封闭式行星传动组成时，传动比可达到i=134-1=28560，即使是如此大的传动比，增加输入端制动器以及末级行星架制动器后，该档的行星机构也能低速随动，当级数增加时，传动比能够更大；需要某一个档位的传动比变得更大，只要增加该档行星减速的级数即可，增加级数后换挡机构的径向尺寸不用加大，其轴向尺寸是各级行星机构轴向尺寸的叠加，相比多平行轴多档变速机构，节省大量的空间；该换挡机构是一个独立的换挡单元，各档相对独立设计，增加或减少档位容易，是一种各档行星机构的轴向叠加或减少，容易实现模块化设计，形成组合同轴线行星传动多档变速传动机构，即提高了设计效率，又提高了生产效率；该机构的多个离合器位置均在输入端，结构容易实现；拓展了行星机构的应用领域。A coaxial planetary transmission multi-speed transmission mechanism is provided, which can realize multi-speed transmission of the coaxial planetary transmission, and the planetary mechanism in the idle gear is in a low-speed follow-up state; the realization range of each gear ratio becomes Larger, for example: when the gear is composed of five-stage closed planetary transmission, the transmission ratio can reach i=13 4 -1=28560, even with such a large transmission ratio, after adding the input brake and the final planet carrier brake , the planetary mechanism of this gear can also follow-up at low speed. When the number of stages increases, the transmission ratio can be larger; if the transmission ratio of a certain gear needs to become larger, just increase the number of planetary reduction stages of this gear, and increase The radial dimension of the shifting mechanism does not need to be enlarged after the number of stages, and its axial dimension is the superposition of the axial dimensions of the planetary mechanisms at all levels, which saves a lot of space compared with the multi-parallel shaft multi-speed transmission mechanism; the shifting mechanism is a Independent shifting unit, each gear is relatively independent design, easy to increase or decrease the gear, it is an axial superposition or reduction of each gear planetary mechanism, easy to realize modular design, forming a combined coaxial planetary transmission multi-speed transmission mechanism , which not only improves the design efficiency, but also improves the production efficiency; the multiple clutch positions of the mechanism are all at the input end, and the structure is easy to realize; the application field of the planetary mechanism is expanded.
附图说明Description of drawings
图1为本实用新型实施例1原理结构示意图；Fig. 1 is a schematic structural diagram of the utility model embodiment 1 principle;
图2为本实用新型实施例2原理结构示意图。Fig. 2 is a schematic structural diagram of the principle of Embodiment 2 of the utility model.
具体实施方式detailed description
实施例1：一种一档为2K-H（A）型、另一档为四级封闭式行星传动的同轴线行星传动二档变速且随动齿轮低速转动机构，它包括输入轴、离合器、制动器、太阳轮、行星轮、行星架、齿圈，行星轮通过轴承分别设置在行星架上，太阳轮通过行星轮与齿圈连接。Embodiment 1: A coaxial planetary transmission with a 2K-H (A) type first gear and a four-stage closed planetary transmission with a second gear speed change and a low-speed rotation mechanism with a follower gear, which includes an input shaft, a clutch , a brake, a sun gear, a planetary gear, a planetary carrier, and a ring gear. The planetary gears are respectively arranged on the planetary carrier through bearings, and the sun gear is connected with the ring gear through a planetary gear.
所述输入轴1与一档离合器4连接，一档离合器4与一档太阳轮6连接，一档输入端制动器Ⅰ5与一档太阳轮6连接，一档太阳轮6与一档行星轮8连接，一档行星轮8与一档齿圈9连接，一档行星轮8设置在一档行星架7上，一档行星架7与一档末级行星架制动器Ⅱ10连接。The input shaft 1 is connected to the first gear clutch 4, the first gear clutch 4 is connected to the first gear sun gear 6, the first gear input end brake I5 is connected to the first gear sun gear 6, and the first gear sun gear 6 is connected to the first gear planetary gear 8 , the first gear planetary gear 8 is connected with the first gear ring gear 9, the first gear planetary gear 8 is set on the first gear planet carrier 7, and the first gear planet carrier 7 is connected with the first gear final stage planet carrier brake II10.
所述输入轴1与二档离合器3连接，二档离合器3与二档一级太阳轮14连接，二档输入端制动器Ⅰ3与一级太阳轮14连接，一级太阳轮14与一级行星轮12连接，一级行星轮12与一级齿圈13连接，一级行星轮12与一级行星架11连接，一级行星架11与二级太阳轮17连接，二级太阳轮17与二级行星轮15连接，二级行星轮15与二级齿圈16连接，二级行星轮15与二级行星架18连接，二级行星架18与三级太阳轮22连接，三级太阳轮22与三级行星轮20连接，三级行星轮20与三级齿圈19连接，三级行星轮20与三级行星架21连接，三级行星架21与四级太阳轮26连接，四级太阳轮26与四级行星轮24连接，四级行星轮24与四级齿圈23连接，四级行星轮24与末级行星架25连接，二档末级行星架25与二档末级行星架制动器Ⅱ27连接。The input shaft 1 is connected to the second gear clutch 3, the second gear clutch 3 is connected to the second gear primary sun gear 14, the second gear input end brake I3 is connected to the primary sun gear 14, and the primary sun gear 14 is connected to the primary planetary gear 12 connection, the primary planetary gear 12 is connected with the primary ring gear 13, the primary planetary gear 12 is connected with the primary planetary carrier 11, the primary planetary carrier 11 is connected with the secondary sun gear 17, and the secondary sun gear 17 is connected with the secondary The planetary gear 15 is connected, the secondary planetary gear 15 is connected with the secondary ring gear 16, the secondary planetary gear 15 is connected with the secondary planetary carrier 18, the secondary planetary carrier 18 is connected with the tertiary sun gear 22, and the tertiary sun gear 22 is connected with the The third-stage planetary gear 20 is connected, the third-stage planetary gear 20 is connected with the third-stage ring gear 19, the third-stage planetary gear 20 is connected with the third-stage planet carrier 21, the third-stage planet carrier 21 is connected with the fourth-stage sun gear 26, and the fourth-stage sun gear 26 is connected with the fourth-stage planetary gear 24, the fourth-stage planetary gear 24 is connected with the fourth-stage ring gear 23, the fourth-stage planetary gear 24 is connected with the final planetary carrier 25, and the second-stage final-stage planetary carrier 25 is connected with the second-stage final-stage planetary carrier brake II 27 connection.
所述的各个行星传动机构的太阳轮为同轴线套装，轴与轴彼此不接触，不影响转动。The sun gears of each of the planetary transmission mechanisms are coaxially fitted, and the shafts do not contact each other and do not affect the rotation.
所述两个档位齿圈9、13、16、19、23一体式连接。The two gear ring gears 9, 13, 16, 19, 23 are integrally connected.
所述一档为2K-H（A）型行星传动、另一档为四级封闭式行星传动的同轴线行星传动二档变速且随动齿轮低速转动机构，两个档位离合器打开，第一档输入端制动器Ⅰ5打开，第二档输入端制动器Ⅰ3闭合，第一档末级行星架制动器Ⅱ10闭合，第二档末级行星架制动器Ⅱ27打开，第一档离合器3闭合，第一档行星传动机构工作，该换挡机构输出第一种转速；第一档离合器3打开，第一档输入端制动器Ⅱ10闭合，第二档输入端制动器Ⅰ5打开，第一档末级行星架制动器Ⅱ10打开，第二档末级行星架制动器Ⅱ27闭合，第二档离合器3闭合，第二档行星传动工作，该换挡机构输出第二种转速。The first gear is a 2K-H (A) type planetary transmission, and the other gear is a coaxial planetary transmission with a four-stage closed planetary transmission. The second gear is variable speed and the follower gear is a low-speed rotation mechanism. The clutches of the two gears are opened, and the second gear is The first gear input brake I5 is opened, the second gear input brake I3 is closed, the first gear final stage planetary carrier brake II10 is closed, the second gear final stage planetary carrier brake II27 is opened, the first gear clutch 3 is closed, and the first gear planetary carrier brake II27 is opened. The transmission mechanism works, and the shifting mechanism outputs the first speed; the clutch 3 of the first gear is opened, the brake II10 of the input end of the first gear is closed, the brake I5 of the input end of the second gear is opened, and the brake II10 of the final stage planetary carrier of the first gear is opened. The final stage planetary carrier brake II 27 of the second gear is closed, the clutch 3 of the second gear is closed, the planetary transmission of the second gear works, and the shifting mechanism outputs the second speed.
所述离合器的类型是啮合式离合器或摩擦式离合器或电磁式离合器或离心摩擦离合器，离合器的操纵方式可以是：M-机动、H-液动、P-气动、E-电动之中任一一种或多种组合形式。The type of clutch is meshing clutch or friction clutch or electromagnetic clutch or centrifugal friction clutch, and the operation mode of the clutch can be any of: M-motor, H-hydraulic, P-pneumatic, E-electric one or more combinations.
有动力输出时，除传递动力的档位外，其余档位的所有转动件均随动，每个档位的输入端制动器与末级行星架制动器协同工作，将原来的高速随动变为低速随动。When there is power output, except for the power transmission gear, all the rotating parts of the other gears follow up, and the input end brake of each gear and the final planetary carrier brake work together to change the original high-speed follow-up into low speed Follow up.
实施例2：一种两个个档位均为2K-H（A）型的同轴线行星传动二档变速且随动齿轮低速转动机构，它包括输入轴、离合器、太阳轮、行星轮、行星架、齿圈，行星轮通过轴承设置在行星架上，太阳轮通过行星轮与齿圈连接。Embodiment 2: A coaxial planetary transmission with two gears of 2K-H (A) type two-speed speed change and follower gear low-speed rotation mechanism, which includes an input shaft, a clutch, a sun gear, a planetary gear, The planetary carrier, the ring gear, and the planetary gear are arranged on the planetary carrier through bearings, and the sun gear is connected with the ring gear through the planetary gear.
所述输入轴1与一档离合器4连接，一档离合器4与一档太阳轮6连接，一档输入端制动器Ⅰ5与一档太阳轮6连接，一档太阳轮6与一档行星轮8连接，一档行星轮8与一档齿圈9连接，一档行星轮8设置在一档行星架7上，一档行星架7与一档末级行星架制动器Ⅱ10连接。The input shaft 1 is connected to the first gear clutch 4, the first gear clutch 4 is connected to the first gear sun gear 6, the first gear input end brake I5 is connected to the first gear sun gear 6, and the first gear sun gear 6 is connected to the first gear planetary gear 8 , the first gear planetary gear 8 is connected with the first gear ring gear 9, the first gear planetary gear 8 is set on the first gear planet carrier 7, and the first gear planet carrier 7 is connected with the first gear final stage planet carrier brake II10.
所述输入轴1与二档离合器2连接，二档离合器2与二档太阳轮14连接，二档输入端制动器Ⅰ3与二档太阳轮14连接，二档太阳轮14与二档行星轮12连接，二档行星轮12与二档齿圈13连接，二档行星轮12设置在二档行星架11上，二档行星架11与二档末级行星架制动器Ⅱ15连接。The input shaft 1 is connected to the second gear clutch 2, the second gear clutch 2 is connected to the second gear sun gear 14, the second gear input end brake I3 is connected to the second gear sun gear 14, and the second gear sun gear 14 is connected to the second gear planetary gear 12 , the second gear planetary gear 12 is connected with the second gear ring gear 13, the second gear planetary gear 12 is arranged on the second gear planet carrier 11, and the second gear planet carrier 11 is connected with the second gear last stage planet carrier brake II15.
所述两个档位齿圈连接。The two gear ring gears are connected.
以上所述实施例并非对本实用新型技术方案保护范围的限制，每一个档位可以是一级行星减速，也可以是多级封闭式行星传动机构，也可以是不同类型行星传动的组合。同一换挡机构中各档的行星传动机构类型可以相同，也可各不相同。当各档减速比相差不是特别大，任意一个档位输入，其余的档位随动，所有随动档转动部件均不超过其允许转速时，所有档位的输入端制动器与末级行星架制动器可以不安装。The above-mentioned embodiments do not limit the scope of protection of the technical solution of the present utility model. Each gear can be a one-stage planetary reduction, or a multi-stage closed planetary transmission mechanism, or a combination of different types of planetary transmissions. The planetary transmission mechanism types of each gear in the same gearshift mechanism can be the same or different. When the reduction ratio of each gear is not particularly large, any gear is input, the rest of the gears follow, and all the rotating parts of the follower gears do not exceed their allowable speeds, the input end brakes of all gears and the final planetary carrier brake You can not install it.
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106286729A (en) * | 2016-09-29 | 2017-01-04 | 泰山医学院 | A kind of many grades of variable transmission mechanisms of coaxial line Gear Planet Transmission |
| CN109505928A (en) * | 2018-12-30 | 2019-03-22 | 苏州富强科技有限公司 | A kind of secondary planetary gear transmission mechanism for 3D bend glass polishing machine |
| WO2023178815A1 (en) * | 2022-03-21 | 2023-09-28 | 赫菲斯科技(深圳)有限公司 | New transmission mechanism and system including planetary gear train, and transmission |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106286729A (en) * | 2016-09-29 | 2017-01-04 | 泰山医学院 | A kind of many grades of variable transmission mechanisms of coaxial line Gear Planet Transmission |
| CN106286729B (en) * | 2016-09-29 | 2018-06-19 | 泰山医学院 | A kind of coaxial line Gear Planet Transmission multi gear variable transmission mechanism |
| CN109505928A (en) * | 2018-12-30 | 2019-03-22 | 苏州富强科技有限公司 | A kind of secondary planetary gear transmission mechanism for 3D bend glass polishing machine |
| WO2023178815A1 (en) * | 2022-03-21 | 2023-09-28 | 赫菲斯科技(深圳)有限公司 | New transmission mechanism and system including planetary gear train, and transmission |
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