CN103332108A - Two-gear power transmission system for BEV integrated planetary gear train - Google Patents
Two-gear power transmission system for BEV integrated planetary gear train Download PDFInfo
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Abstract
本发明涉及一种纯电动汽车集成式行星轮系的两档动力传动系统。包括驱动电机、两档行星轮系变速器、带同步器的换档机构、差速器、左半轴和右半轴,其中两档行星轮系变速器是由第一级行星轮系和第二级行星轮系串联构成,驱动电机、两档行星轮系变速器和差速器集成为一体,且驱动电机、两档行星轮系变速器和差速器三者的轴线在同一条直线上,通过带同步器的换档机构,实现低档、高档和空档的平顺切换,本发明的一种专为纯电动汽车设计的集成式行星轮系的两档动力传动系统,设计独特、结构紧凑、传动效率高,便于整车布置和轻量化,兼顾了整车动力性、经济性和舒适性的要求,从而有利于产业化推广。
The invention relates to a two-speed power transmission system of an integrated planetary gear train of a pure electric vehicle. Including drive motor, two-speed planetary gear transmission, shifting mechanism with synchronizer, differential, left half shaft and right half shaft, where the two-speed planetary gear transmission is composed of the first-stage planetary gear The planetary gear train is formed in series, the driving motor, the two-speed planetary gear transmission and the differential are integrated into one, and the axes of the driving motor, the two-speed planetary gear transmission and the differential are on the same straight line, through the belt synchronous The shift mechanism of the gear shifter realizes the smooth switching of low gear, high gear and neutral gear. The two-speed power transmission system of the integrated planetary gear train specially designed for pure electric vehicles of the present invention has unique design, compact structure and high transmission efficiency. , which is convenient for vehicle layout and light weight, and takes into account the requirements of vehicle power, economy and comfort, which is conducive to the promotion of industrialization.
Description
技术领域 technical field
本发明涉及一种电动汽车动力传动系统,具体是涉及一种纯电动汽车集成式行星轮系的两档动力传动系统,属于电动汽车动力传输技术领域。 The invention relates to a power transmission system of an electric vehicle, in particular to a two-speed power transmission system of an integrated planetary gear train of a pure electric vehicle, and belongs to the technical field of power transmission of electric vehicles.
背景技术 Background technique
为了解决世界的能源和环保问题,电动汽车的研发已成为汽车工业发展和研究的热点。鉴于纯电动汽车动力传动系统主要部件(驱动电机、变速器和差速器)在研发过程中缺乏统一的设计布置,致使动力传动系统结构复杂、体积庞大、重量增加、系统分散、成本较高,不利于其研制和产业化,将驱动电机、变速器、差速器集成化是纯电动汽车发展的必然选择。目前电动汽车集成式动力传动系统多采用平行轴输出结构,这种结构实现简单,技术成熟,但驱动电机和变速器相对差速器和半轴偏心设置,给动力传动系统的布置设计带来很大的难度。此外,目前纯电动汽车或者采用燃油汽车自动变速器,使得传动系统结构复杂,整车质量增加,降低了能量利用效率,或者采用单一固定速比的减速器,使得驱动电机常常工作在低效率区,整车续驶里程减少,且很难兼顾整车动力性和经济性的要求,尚没有适用于纯电动汽车的集成变速驱动系统。 In order to solve the world's energy and environmental protection problems, the research and development of electric vehicles has become a hot spot in the development and research of the automobile industry. In view of the lack of unified design and layout of the main components of the pure electric vehicle power transmission system (drive motor, transmission and differential) during the research and development process, the power transmission system has a complex structure, bulky volume, increased weight, scattered systems, and high costs. Conducive to its development and industrialization, the integration of drive motors, transmissions, and differentials is an inevitable choice for the development of pure electric vehicles. At present, the integrated power transmission system of electric vehicles mostly adopts a parallel shaft output structure. This structure is simple to implement and the technology is mature, but the drive motor and transmission are set eccentrically with respect to the differential and the half shaft, which brings a great deal to the layout design of the power transmission system. difficulty. In addition, the current pure electric vehicles or automatic transmissions for fuel vehicles make the structure of the transmission system complex, increase the mass of the vehicle, and reduce energy utilization efficiency, or use a single fixed speed ratio reducer, so that the drive motor often works in the low efficiency area. The mileage of the vehicle is reduced, and it is difficult to balance the power and economy requirements of the vehicle. There is no integrated variable speed drive system suitable for pure electric vehicles.
专利CN102616134A公开一种纯电动汽车用集成驱动装置,该装置将驱动、减速、差速机构集成一体,减少了体积,提高了空间利用率。该装置采用一档固定速比的双行星排齿轮减速机构,很难兼顾整车最高车速和最大爬坡度,以及动力性和经济性的要求。 Patent CN102616134A discloses an integrated drive device for pure electric vehicles, which integrates drive, deceleration and differential mechanisms, reduces volume and improves space utilization. The device adopts a double-planetary gear reduction mechanism with a fixed speed ratio, and it is difficult to balance the maximum vehicle speed and maximum gradient, as well as the requirements of power and economy.
专利CN102555794A公开了一种电动汽车行星轮系变速驱动系统,包括驱动电机、离合器、行星轮系变速机构、差速器、减速齿轮传动机构和车轮。该系统驱动电机、行星轮系变速机构、差速器的主轴位于与车轮轴线平行的同一条直线上,通过离合器主动盘与两个离合器从动盘的不同配合形式来实现两档变速。但该系统行星轮系变速机构和减速齿轮传动机构分离,且为平行轴结构,动力传递路线过长,增加了驱动系统本身结构的复杂性,体积尺寸大。 Patent CN102555794A discloses a planetary gear train variable speed drive system for an electric vehicle, including a drive motor, a clutch, a planetary gear train speed change mechanism, a differential, a reduction gear transmission mechanism and wheels. The system drives the motor, planetary gear train transmission mechanism, and the main shaft of the differential are located on the same straight line parallel to the wheel axis, and two-speed transmission is realized through the different cooperation forms of the clutch driving disc and the two clutch driven discs. However, the planetary gear train transmission mechanism and reduction gear transmission mechanism of this system are separated, and have a parallel shaft structure, and the power transmission route is too long, which increases the complexity of the structure of the drive system itself and has a large size.
专利CN102259588A公开了电动汽车一体化驱动装置,该装置由变速器、减速器、差速器及共用的铝合金外壳和换挡机构组成,采用同步器完成档位变换,不需离合器使结构简化。但其变速机构为平行轴结构,存在着外形尺寸大,给整车的布置带来不便。 Patent CN102259588A discloses an integrated drive device for electric vehicles, which is composed of a transmission, a reducer, a differential, and a shared aluminum alloy casing and a shifting mechanism. A synchronizer is used to complete gear shifting, and the structure is simplified without a clutch. However, its speed change mechanism is a parallel shaft structure, which has a large external dimension, which brings inconvenience to the layout of the whole vehicle.
因此,鉴于驱动电机特性和燃油发动机特性的不同,需要提供一种纯电动汽车集成式两档动力传动系统,使其不仅能够适时地根据车况、路况和驾驶员的主观愿望进行平顺换档,而且能够保持驱动电机处于效率高的工作区域,充分发挥电动汽车节能环保的优势。 Therefore, in view of the difference in the characteristics of the drive motor and the fuel engine, it is necessary to provide an integrated two-speed power transmission system for pure electric vehicles, so that it can not only perform smooth shifts in due time according to vehicle conditions, road conditions and the driver's subjective wishes, but also It can keep the driving motor in a high-efficiency working area, and give full play to the advantages of electric vehicles in energy saving and environmental protection.
发明内容 Contents of the invention
为解决上述现有技术存在的缺陷或不足,本发明提供一种将驱动电机、两档行星轮系变速器和差速器集成为一体的纯电动汽车集成式行星轮系的两档动力传动系统。 In order to solve the above defects or deficiencies in the prior art, the present invention provides a two-speed power transmission system of a pure electric vehicle integrated planetary gear train that integrates a drive motor, a two-speed planetary gear train transmission and a differential.
本发明是通过以下技术方案来实现的: The present invention is achieved through the following technical solutions:
本发明的一种纯电动汽车集成式行星轮系的两档动力传动系统包括驱动电机、变速器、带同步器的换档机构、差速器、左半轴和右半轴,驱动电机的输出轴的输出端伸至电机壳体外部;差速器包括差速器壳、行星轮轴、差速器行星轮、左半轴齿轮、右半轴齿轮,左半轴齿轮和右半轴齿轮之间通过行星轮轴分别设有两只差速器行星轮,行星轮轴的两端分别设于差速器壳上。 A two-speed power transmission system of a pure electric vehicle integrated planetary gear train of the present invention includes a drive motor, a transmission, a shift mechanism with a synchronizer, a differential, a left half shaft and a right half shaft, and an output shaft of the drive motor The output end extends to the outside of the motor housing; the differential includes a differential case, a planetary shaft, a differential planetary wheel, a left side gear, a right side gear, and between the left side gear and the right side gear Two differential planetary gears are respectively arranged through the planetary gear shafts, and the two ends of the planetary gear shafts are respectively arranged on the differential gear case.
本发明的变速器为由第一级行星轮系和第二级行星轮系串联构成的两档行星轮系变速器,包括圆柱管状的变速器壳体。 The transmission of the present invention is a two-speed planetary gear transmission composed of a first-stage planetary gear train and a second-stage planetary gear train in series, and includes a cylindrical tubular transmission housing.
所述驱动电机的输出轴为空心轴,所述输出轴的外伸端上固定设有第一级太阳轮,与第一级太阳轮对应设有第一级齿圈,所述第一级齿圈设于变速器壳体的一端内,第一级太阳轮和第一级齿圈之间通过第一级行星架配合设有三只第一级行星轮;第一级太阳轮、第一级齿圈、第一级行星架和三只第一级行星轮构成第一级行星轮系;三只第一级行星轮位于第一级行星架的轴向一侧,第一级行星架的轴向另一侧为第一管轴,第一级行星架的第一管轴作为第一级行星轮系的输出轴,第一级行星架的第一管轴上通过花键配合设有第二级太阳轮;与第二级太阳轮对应设有第二级齿圈;第二级太阳轮和第二级齿圈之间通过第二级行星架配合设有三只第二级行星轮,第二级太阳轮、第二级齿圈、第二级行星架和三只第二级行星轮构成第二级行星轮系;第一级行星轮系和第二级行星轮系串联构成两档行星轮系变速器;三只第二级行星轮位于第二级行星架的轴向一侧,第二级行星架的轴向另一侧为第二管轴,第二级行星架的第二管轴为第二级行星轮系的输出轴;所述第二级齿圈的轴向一侧为第三管轴,所述第三管轴套设在第二级行星架的第二管轴上,即第二级行星架的第二管轴穿过第三管轴;第一级行星轮系和第二级行星轮系均位于变速器壳体内,与第一级齿圈对应的变速器壳体的一端连接着驱动电机的机壳端面,变速器壳体的另一端设有端盖,所述第三管轴和第二管轴均伸至端盖外部;第一接合齿圈设在变速器壳体端盖上,第二接合齿圈通过花键配合套设在第二管轴上,第一接合齿圈和第二接合齿圈之间的同步器通过花键配合套设在第三管轴上,所述同步器为锁环式惯性同步器,包括同步环、接合套、滑块和花键毂;第二级齿圈的第三管轴通过花键配合连接着花键毂;与同步器配合设有换档拨叉;第二接合齿圈外侧的第二级行星架的第二管轴通过花键连接着差速器壳,差速器壳内设有左半轴和右半轴,左半轴穿过第二级行星架的第二管轴、第一级行星架的第一管轴和驱动电机轴,并与车辆左侧车轮连接,右半轴与车辆右侧车轮连接,且左半轴和右半轴同轴,左半轴齿轮设于左半轴上,右半轴齿轮设于右半轴上;驱动电机的输出轴的轴线、两档行星轮系变速器的轴线和差速器的左半轴和右半轴的轴线在同一条直线上。 The output shaft of the drive motor is a hollow shaft, and a first-stage sun gear is fixed on the extended end of the output shaft, and a first-stage ring gear is provided corresponding to the first-stage sun gear. The first-stage gear The ring is set in one end of the transmission housing, and three first-stage planetary gears are arranged between the first-stage sun gear and the first-stage ring gear through the first-stage planet carrier; the first-stage sun gear, the first-stage ring gear , the first-stage planet carrier and three first-stage planetary gears constitute the first-stage planetary gear train; the three first-stage planetary wheels are located on one axial side of the first-stage planetary carrier, and the axial direction of the first-stage planetary carrier is on the other One side is the first tube shaft, the first tube shaft of the first-stage planet carrier is used as the output shaft of the first-stage planetary gear train, and the second-stage sun is arranged on the first tube shaft of the first-stage planet carrier through spline fit. There is a second-stage ring gear corresponding to the second-stage sun gear; three second-stage planetary gears are arranged between the second-stage sun gear and the second-stage ring gear through the second-stage planet carrier, and the second-stage sun gear Wheel, second-stage ring gear, second-stage planet carrier and three second-stage planetary gears constitute the second-stage planetary gear train; the first-stage planetary gear train and the second-stage planetary gear train are connected in series to form a two-speed planetary gear train transmission ;Three second-stage planetary gears are located on one axial side of the second-stage planet carrier, the other axial side of the second-stage planet carrier is the second tube axis, and the second tube axis of the second-stage planet carrier is the second The output shaft of the first-stage planetary gear train; the axial side of the second-stage ring gear is the third tube shaft, and the third tube shaft is sleeved on the second tube shaft of the second-stage planetary carrier, that is, the second The second tube shaft of the first-stage planetary carrier passes through the third tube shaft; the first-stage planetary gear train and the second-stage planetary gear train are both located in the transmission case, and one end of the transmission case corresponding to the first-stage ring gear is connected to the drive The end face of the casing of the motor and the other end of the transmission casing are provided with an end cover, and the third tube shaft and the second tube shaft both extend to the outside of the end cover; the first engagement ring gear is arranged on the end cover of the transmission case, and the second The two engaging ring gears are sleeved on the second tubular shaft through spline fit, and the synchronizer between the first engaging ring gear and the second engaging ring gear is sleeved on the third tubular shaft through spline fit, and the synchronizer It is a lock ring type inertial synchronizer, including a synchronous ring, an adapter sleeve, a slider and a spline hub; the third tube shaft of the second stage ring gear is connected to the spline hub through spline fit; it is equipped with a shift gear in conjunction with the synchronizer Shift fork; the second tube shaft of the second-stage planetary carrier outside the second engaging ring gear is connected to the differential case through a spline, and the left half shaft and the right half shaft are arranged in the differential case, and the left half shaft passes through The second tube shaft of the second-stage planetary carrier, the first tube shaft of the first-stage planetary carrier and the drive motor shaft are connected with the left wheel of the vehicle, the right half shaft is connected with the right side wheel of the vehicle, and the left half shaft and the right The half-shafts are coaxial, the left half-shaft gear is set on the left half-shaft, and the right half-shaft gear is set on the right half-shaft; the axis of the output shaft of the drive motor, the axis of the two-speed planetary gear transmission and the left half of the differential The axes of the axis and the right half axis are on the same straight line. the
第一级行星轮系和第二级行星轮系之间的变速器壳体中部径向设有环状的加强筋板,以支撑变速器中的传动部件。 The middle part of the transmission housing between the first-stage planetary gear train and the second-stage planetary gear train is radially provided with annular stiffeners to support the transmission components in the transmission.
本发明的有益技术效果在于: The beneficial technical effects of the present invention are:
1. 本发明集驱动电机、两档行星轮系变速器和差速器为一体,且驱动电机、两档行星轮系变速器和差速器三者的轴线在同一条直线上,与动力部件分置的动力传动系统相比,集成度高,传动路线短,体积小和质量轻,且有利于整车的设计布置和轻量化; 1. The present invention integrates the driving motor, the two-speed planetary gear transmission and the differential, and the axes of the driving motor, the two-speed planetary gear transmission and the differential are on the same straight line, separated from the power components Compared with the traditional power transmission system, it has high integration, short transmission line, small size and light weight, and is conducive to the design layout and lightweight of the whole vehicle;
2. 本发明采用两档行星轮系变速机构,通过带同步器的换档机构实现低档、高档和空档的平顺切换,省去了传统汽车驱动桥中的主减速机构,结构紧凑、质量轻、转动平稳,与一档固定速比的电动汽车变速机构相比,能够提高整车动力性、驱动电机效率、动力电池寿命和延长整车续驶里程。 2. The present invention adopts a two-speed planetary gear transmission mechanism, and realizes smooth switching between low gear, high gear and neutral gear through a gear shift mechanism with a synchronizer, eliminating the need for the main deceleration mechanism in a traditional automobile drive axle, with compact structure and light weight , The rotation is stable, compared with the electric vehicle transmission mechanism with a fixed speed ratio of the first gear, it can improve the power performance of the vehicle, the efficiency of the driving motor, the life of the power battery and prolong the mileage of the vehicle.
附图说明 Description of drawings
图1为本发明结构示意图。 Fig. 1 is a schematic diagram of the structure of the present invention.
图2是本发明低档(Ⅰ档)状态示意图。 Fig. 2 is a schematic diagram of the low gear (I gear) state of the present invention.
图3是本发明高档(Ⅱ档)状态示意图。 Fig. 3 is a schematic diagram of the high-grade (II gear) state of the present invention.
图4是本发明空档状态示意图。 Fig. 4 is a schematic diagram of the neutral state of the present invention.
上图中序号:1.驱动电机,2.输出轴,3.第一级太阳轮,4.第一级行星架,5.第一级行星轮,6.第一级齿圈,7.第二级太阳轮,8.第二级行星轮,9.第二级行星架,10.第二级齿圈,11.第一接合齿圈,12.换档拨叉,13.同步环,14.接合套,15.滑块,16.花键毂,17.第二接合齿圈,18.差速器壳,19.行星轮轴,20.差速器行星轮,21.右半轴齿轮,22.右半轴,23.左半轴齿轮,24. 左半轴,25. 变速器壳体。 Serial numbers in the above picture: 1. Drive motor, 2. Output shaft, 3. First-stage sun gear, 4. First-stage planet carrier, 5. First-stage planetary gear, 6. First-stage ring gear, 7. First-stage 2nd stage sun gear, 8. 2nd stage planetary gear, 9. 2nd stage planet carrier, 10. 2nd stage ring gear, 11. 1st engagement ring gear, 12. Shift fork, 13. Synchronization ring, 14 .Joint sleeve, 15. Slider, 16. Spline hub, 17. Second joint ring gear, 18. Differential case, 19. Planetary gear shaft, 20. Differential planetary gear, 21. Right side shaft gear, 22. Right half shaft, 23. Left half shaft gear, 24. Left half shaft, 25. Transmission case.
具体实施方式 Detailed ways
下面结合附图,通过实施例对本发明作进一步地描述。 The present invention will be further described through the embodiments below in conjunction with the accompanying drawings.
实施例 Example
参见图1,一种纯电动汽车集成式行星轮系的两档动力传动系统包括驱动电机1、两档行星轮系变速器、带同步器的换档机构、差速器、左半轴24和右半轴22。差速器包括差速器壳18、行星轮轴19、差速器行星轮20、左半轴齿轮23、右半轴齿轮21,左半轴齿轮23和右半轴齿轮21之间通过行星轮轴19分别设有两只差速器行星轮20,行星轮轴19的两端分别设于差速器壳18上。
Referring to Fig. 1, a two-speed power transmission system of a pure electric vehicle integrated planetary gear train includes a
由图1可见,驱动电机1的输出轴2为空心轴,输出轴2的输出端伸至电机壳体外部;输出轴2的外伸端上固定安装有第一级太阳轮3,与第一级太阳轮3对应设有第一级齿圈6,第一级齿圈6设于圆柱管状的变速器壳体25的一端内,第一级太阳轮3和第一级齿圈6之间通过第一级行星架4配合安装有三只第一级行星轮5;第一级太阳轮3、第一级齿圈6、第一级行星架4和三只第一级行星轮5构成第一级行星轮系。三只第一级行星轮5位于第一级行星架4的轴向一侧,第一级行星架4的轴向另一侧为第一管轴;第一级行星架4的第一管轴作为第一级行星轮系的输出轴,第一级行星架4的第一管轴上通过花键配合安装有第二级太阳轮7;与第二级太阳轮7对应设有第二级齿圈10;第二级太阳轮7和第二级齿圈10之间通过第二级行星架9配合安装有三只第二级行星轮8,第二级太阳轮7、第二级齿圈10、第二级行星架9和三只第二级行星轮8构成第二级行星轮系;第一级行星轮系和第二级行星轮系串联构成两档行星轮系变速器。三只第二级行星轮8位于第二级行星架9的轴向一侧,第二级行星架9的轴向另一侧为第二管轴,第二级行星架9的第二管轴作为第二级行星轮系的输出轴;第二级齿圈10的轴向一侧为第三管轴,第三管轴套设在第二级行星架9的第二管轴上,即第二级行星架9的第二管轴穿过第三管轴;第一级行星轮系和第二级行星轮系均位于变速器壳体25内,第一级齿圈6一侧的变速器壳体25的一端连接着驱动电机1的机壳端面,变速器壳体25的另一端安装有端盖,第三管轴和第二管轴均伸至端盖外部;第一接合齿圈11设在变速器壳体25端盖上,第二接合齿圈17通过花键配合套设在第二管轴上,第一接合齿圈11和第二接合齿圈17之间的同步器通过花键配合套设在第三管轴上,所述同步器为锁环式惯性同步器,包括同步环13、接合套14、滑块15和花键毂16,第二级齿圈10的第三管轴通过花键配合连接着花键毂16;与同步器配合安装有换档拨叉12;第二接合齿圈17外侧的第二级行星架9的第二管轴通过花键连接着差速器壳18;差速器壳18内设有左半轴24和右半轴22,左半轴24穿过第二级行星架9的第二管轴、第一级行星架4的第一管轴和驱动电机的输出轴2,并与车辆左侧车轮连接,右半轴22与车辆右侧车轮连接,且左半轴24和右半轴22同轴,左半轴齿轮23安装于左半轴24上,右半轴齿轮21安装于右半轴22上;驱动电机1的输出轴2的轴线、两档行星轮系变速器的轴线和差速器的左半轴24和右半轴22的轴线在同一条直线上。
It can be seen from Figure 1 that the
第一级行星轮系和第二级行星轮系之间的变速器壳体25中部径向设有环状的加强筋板,以支撑变速器中的传动部件。
The middle part of the
本发明的工作原理如下: The working principle of the present invention is as follows:
以实际开发某型纯电动汽车两档动力传动系统为例,本发明的一种纯电动汽车集成式行星轮系的两档动力传动系统省去了传统汽车传动系中离合器和驱动桥中的主减速机构等,Ⅰ档传动比为10.2,Ⅱ档传动比为3.4,两档行星轮系变速器和差速器各传动齿轮的齿数如表1所示。 Taking the actual development of a two-speed power transmission system of a certain type of pure electric vehicle as an example, the two-speed power transmission system of a pure electric vehicle integrated planetary gear train of the present invention eliminates the need for clutches and drive axles in the traditional vehicle transmission system. The reduction mechanism, etc., the transmission ratio of the first gear is 10.2, and the transmission ratio of the second gear is 3.4. The number of teeth of each transmission gear of the two-speed planetary gear train transmission and the differential is shown in Table 1.
表1 齿轮齿数表 Table 1 Gear teeth table
当驱动电机1驱动第一级太阳轮3转动时,两档行星轮系变速器通过换档拨叉12拨动接合套14,在滑块15和同步环13共同作用下,分别与第一接合齿圈11、第二接合齿圈17啮合,实现低档、高档和空档的平顺切换,并将动力传给差速器壳18,带动左半轴24和右半轴22转动,进而驱动车辆实现低速行驶、高速行驶、制动、倒车和拖车运行工况。
When the
本发明的一种纯电动汽车集成式行星轮系的两档动力传动系统在低速行驶、高速行驶、制动行驶、倒车行驶和拖车行驶等工况下的工作过程是: The working process of the two-speed power transmission system of a pure electric vehicle integrated planetary gear train of the present invention under low-speed driving, high-speed driving, braking, reversing and trailer driving is as follows:
1.车辆起步和爬坡低速行驶时,集成式行星轮系的两档动力传动系统处在低档(Ⅰ)运行状态。通过换档拨叉12拨动接合套14向低档的第一接合齿圈11移动,即接合套14滑向左边,完成挂档,如图2所示。驱动电机1输出相应的转矩和转速,并经两档行星轮系变速器、差速器壳18和左半轴24、右半轴22驱动车辆实现低速行驶。其动力传递路径为:
1. When the vehicle starts and climbs at low speed, the two-speed power transmission system of the integrated planetary gear train is in the low gear (I) operating state. The
驱动电机1的输出轴2→第一级太阳轮3→第一级行星架4→第二级太阳轮7→第二级行星架9→差速器壳18→左半轴24、右半轴22→左、右车轮;
此时第二级齿圈10通过同步器的接合套14与第一接合齿圈11啮合,因第一接合齿圈11与变速器壳体25端盖固接为固定件,第二级齿圈10的第三管轴的转速为零,故此时两档行星轮系变速器的传动比可表示为:
At this time, the second-
(1) (1)
式中 Za1-第一级太阳轮3的齿数; Zb1-第一级齿圈6的齿数;Za2-第二级太阳轮7的齿数;Zb2-第二级齿圈10的齿数;
In the formula Z a1 - the number of teeth of the first
2.车辆高速行驶时,集成式行星轮系的两档动力传动系统处在高档(Ⅱ)运行状态。通过换档拨叉12拨动接合套14向高档的第二接合齿圈17移动,即接合套14滑向右边,完成挂档,如图3所示。驱动电机1输出相应的转矩和转速,并经两档行星轮系变速器、差速器壳18和左半轴24、右半轴22驱动车辆实现高速行驶。其动力传递路径为:
2. When the vehicle is running at high speed, the two-speed power transmission system of the integrated planetary gear train is in the high-grade (II) operating state. The
驱动电机1的输出轴2→第一级太阳轮3→第一级行星架4→第二级太阳轮7→第二级行星架9→差速器壳18→左半轴24、右半轴22→左、右车轮;
此时第二级齿圈10通过同步器的接合套14与第二接合齿圈17啮合,第二级齿圈10的第三管轴和第二级行星架9的第二管轴闭锁而整体旋转,并与第一级行星架4的第一管轴同步旋转,故此时两挡行星轮系变速器的传动比可表示为:
At this time, the second-
(2) (2)
3.在制动能量回收时,集成式行星轮系的两档动力传动系统处在低档(Ⅰ)运行状态。动力传递路径与低速行驶工况相同,如图2所示,驱动电机1处于发电状态,实现能量回收;
3. During braking energy recovery, the two-speed power transmission system of the integrated planetary gear train is in the low gear (I) operating state. The power transmission path is the same as the low-speed driving condition. As shown in Figure 2, the driving
4.倒车低速行驶时,集成式行星轮系的两档动力传动系统处在低档(Ⅰ)运行状态,如图2所示,此时驱动电机1反转,实现车辆倒车行驶;
4. When reversing and driving at low speed, the two-speed power transmission system of the integrated planetary gear train is in the low-gear (I) operating state, as shown in Figure 2, at this time, the
5.车辆在运行过程中发生故障需要拖行时,此时驱动电机1进入自由模式工作状态。通过换档拨叉12带动接合套14轴向移动,完成摘空档分离,使各部件处于独立状态,并断电,实现空档状态下的拖车行驶,如图4所示。
5. When the vehicle breaks down and needs to be towed during operation, the
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