WO2009049514A1 - Transmission mécanique-hydraulique à variation continue, procédé associé, et transmission mécanique-hydraulique à variation continue pour véhicule - Google Patents

Transmission mécanique-hydraulique à variation continue, procédé associé, et transmission mécanique-hydraulique à variation continue pour véhicule Download PDF

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Publication number
WO2009049514A1
WO2009049514A1 PCT/CN2008/072356 CN2008072356W WO2009049514A1 WO 2009049514 A1 WO2009049514 A1 WO 2009049514A1 CN 2008072356 W CN2008072356 W CN 2008072356W WO 2009049514 A1 WO2009049514 A1 WO 2009049514A1
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WO
WIPO (PCT)
Prior art keywords
turbine
power input
hydraulic
input shaft
plate
Prior art date
Application number
PCT/CN2008/072356
Other languages
English (en)
French (fr)
Inventor
Haiping Liu
Original Assignee
Haiping Liu
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Haiping Liu filed Critical Haiping Liu
Publication of WO2009049514A1 publication Critical patent/WO2009049514A1/zh
Priority to US12/756,198 priority Critical patent/US8282522B2/en

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/06—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/10—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of fluid gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
    • F16H47/06—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H29/00—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action
    • F16H29/12—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between rotary driving and driven members
    • F16H29/16—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between rotary driving and driven members in which the transmission ratio is changed by adjustment of the distance between the axes of the rotary members
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19149—Gearing with fluid drive

Definitions

  • the present invention relates to a continuously variable transmission, and more particularly to a mechanical hydraulic continuously variable transmission and a mechanical hydraulic continuously variable transmission method, and a mechanical hydraulic continuously variable transmission for use in a vehicle.
  • the torque converter has good adaptability and variable speed torque change function. It has buffering and damping effect on the transmission system, no mechanical wear, high reliability and long service life. It is used in various vehicles and engineering. Machinery, construction machinery and other mechanical fields have been widely used.
  • the torque converter has a contradiction between the torque-changing ability and the transmission efficiency. In many cases, the start-up is slow and the output torque cannot meet the requirements. In the case of large torque converter, the transmission efficiency of the small gear ratio is very low, the heating of the equipment needs to increase the cooling system, making the system structure complex and bulky.
  • the hydraulic automatic transmission consists of a torque converter and a planetary gear transmission or a parallel shaft gear transmission.
  • the torque converter can automatically and steplessly change the torque ratio within a certain range, but its torque coefficient is not large enough, and the transmission efficiency is low at a small speed ratio, and there is a contradiction between the torque capacity and the transmission efficiency. Therefore, it needs to be used with a gear transmission.
  • gear shifting gears both lose efficiency and lose speed, and add a lot of clutches, brakes, and control mechanisms to match the shift, making the transmission heavy, complicated, and bulky.
  • the sinusoidal continuously variable transmission is a new principle of continuously variable transmission, which can realize zero starting, stepless speed change and very large starting torque.
  • the torque ratio is very large, the work efficiency is high, the structure is simple, the volume is small, and the weight is light.
  • the technical problem to be solved by the present invention is to provide a combination of mechanical torque and hydraulic force in many cases of the above-mentioned torque converter of the prior art that the start-up is slow and the output torque cannot meet the requirements.
  • a mechanical hydraulic continuously variable transmission and method that has the advantages of a moment.
  • Another technical problem to be solved by the present invention is to provide a combination of mechanical torque in many cases of the above-mentioned hydraulic torque converter for automobiles of the prior art that the start-up is slow and the output torque cannot meet the requirements.
  • the technical solution adopted by the present invention to solve the technical problem thereof is: providing a mechanical hydraulic continuously variable transmission comprising a mechanical shifting assembly and a hydraulic shifting assembly which are sequentially mounted on a power input shaft and disposed in the outer casing ;
  • the mechanical shifting assembly includes an eccentric mechanism that rotates with the power input shaft, a push plate rotatably mounted on the eccentric mechanism, is disposed on one side of the push plate, and is fixed to the inside of the case a fixed disk, and a drive plate disposed on the other side of the push plate and rotatably mounted on the power input shaft; the eccentric mechanism adjusts the push plate according to a load of the drive plate a eccentricity between the power input shafts; a slider assembly for transmitting power between the fixed plate and the pressing plate; and between the pressing plate and the driving plate;
  • the hydraulic shifting assembly includes a pump impeller fixedly coupled to the power input shaft, and a turbine fixedly coupled to the drive disc; a transmission medium that transmits power between the pump impeller and the turbine
  • the turbine is provided with a power take-off shaft that extends out of the outer casing.
  • the turbine is located between the drive plate and the impeller, and the turbine is fixedly coupled to the drive plate via a turbine inner sleeve.
  • a guide wheel is provided between the turbine and the pump impeller; and the guide wheel is mounted on the inner bushing of the turbine via a one-way clutch or a bearing.
  • the urging disk is mounted on the eccentric mechanism by a bearing, and the turbine inner bushing is mounted on the power input shaft through a bearing;
  • the eccentricity The mechanism is a hydraulic propulsion eccentric mechanism;
  • the eccentricity of the eccentric mechanism is zero ⁇ , the driving disc and the pressing disc are concentric with the power input shaft; when the eccentric mechanism is loaded with the load on the turbine output shaft, an eccentric amount is generated.
  • the push plate and the drive plate are eccentric.
  • the mechanical shifting assembly includes an eccentric mechanism that rotates with the power input shaft, a pushing plate rotatably mounted on the eccentric mechanism, is disposed on one side of the pressing plate, and is fixed to the inner side of the outer casing a fixed disk, and a drive plate disposed on the other side of the push plate and rotatably mounted on the power input shaft; the eccentric mechanism adjusts the push plate according to a load of the drive plate a eccentricity between the power input shafts; a slider assembly for transmitting power between the fixed plate and the pressing plate; and between the pressing plate and the driving plate;
  • the hydraulic shifting assembly includes a pump impeller fixedly coupled to the power input shaft, and a turbine fixedly coupled to the drive disc; a transmission medium that transmits power between the pump impeller and the turbine The turbine is provided with a turbine output shaft;
  • the gear shifting assembly includes a sun gear fixedly coupled to the turbine output shaft, a planetary gear meshing with the sun gear, an internal spur meshing with the planetary gear, and a planet for mounting the planetary gear a carrier, a clutch disposed outside the turbine output shaft, and a brake disposed inside the outer casing, the clutch and the brake controlling the carrier, the inner sprocket having a power output shaft extending from the outer casing.
  • the turbine is located between the drive plate and the impeller, and the turbine is fixedly coupled to the drive plate via a turbine inner sleeve.
  • a guide wheel is disposed between the turbine and the pump impeller; and the guide wheel is mounted on the inner bushing of the turbine via a one-way clutch or a bearing.
  • a lockup clutch is disposed between the power input shaft and the turbine output shaft;
  • the pressing plate is mounted on the eccentric mechanism through a bearing
  • the inner bush sleeve is mounted on the power input shaft through a bearing
  • the eccentric mechanism is a hydraulic force pushing eccentric mechanism
  • the eccentricity of the eccentric mechanism is zero, and the driving disc and the pressing disc are concentric with the power input shaft; when the eccentric mechanism has a load on the output shaft of the turbine, an eccentric amount is generated.
  • the push plate and the drive plate are eccentric.
  • the present invention also provides a mechanical hydraulic stepless shifting method, comprising the following steps:
  • the implementation of the present invention has the following beneficial effects: By adding a mechanical shifting assembly to the front stage of the hydraulic shifting assembly, and utilizing the advantage of the mechanical shifting assembly having a large torque ratio at a small speed, the turbine of the hydraulic shifting assembly is quickly driven. Start up, and accelerate the rotation very quickly; and when the speed ratio reaches a certain level, the pump-to-turbine of the hydraulic shifting unit becomes the main power transmission route, thus integrating the mechanical speed change component with a small speed ratio and having a large torque ratio and high
  • the advantages of efficiency and the advantages of the high speed ratio of the hydraulic shifting unit to the high efficiency work organically combine the advantages of both, and have the advantages of efficient transmission under various operating conditions.
  • FIG. 1 is a schematic structural view of a mechanical hydraulic continuously variable transmission according to the present invention
  • FIG. 2 is a schematic structural view of an eccentric mechanism of the mechanical hydraulic continuously variable transmission of the present invention
  • FIG. 3 is a schematic structural view of a vehicle hydraulic hydraulic continuously variable transmission of the present invention.
  • FIG. 4 is a schematic diagram of a power transmission path of a vehicle in a forward speed D using a vehicular hydraulic hydraulic continuously variable transmission of the present invention
  • FIG. 5 is a schematic diagram of a power transmission path of a vehicle in a reverse gear R using the vehicular hydraulic hydraulic continuously variable transmission of the present invention
  • FIG. 6 is a schematic diagram of a power transmission path of a vehicle in a parking range P using the vehicular hydraulic hydraulic continuously variable transmission of the present invention
  • Fig. 7 is a schematic view showing a power transmission path of a vehicle in a neutral position N using the vehicular hydraulic hydraulic continuously variable transmission of the present invention.
  • an embodiment of a mechanical hydraulic continuously variable transmission of the present invention includes a mechanical shifting assembly and a hydraulic shifting assembly that are sequentially mounted on the power input shaft 1 and disposed within the outer casing.
  • the housing is used to mount the entire transmission in the proper position, and its shape and structure can be designed according to actual requirements.
  • the housing is coupled to the power input shaft 1 and the turbine output shaft 12 of the hydraulic shifting assembly via bearings.
  • the mechanical shifting assembly includes an eccentric mechanism that rotates with the power input shaft 1, a push plate 4 that is mounted on the eccentric mechanism 2 by bearings, a fixed plate 3 that is fixedly mounted inside the outer casing, and a rotatably mounted power input Drive plate 5 on shaft 1.
  • the fixed disk 3 and the driving plate 5 are respectively located on both sides of the pressing plate 4, and between the pressing plate 4 and the fixed plate 3, and between the pressing plate 4 and the driving plate 5 are connected by a slider assembly to transmit power.
  • the structural form of the fixed disk 3, the push plate 4, the drive plate 5 and the slider assembly can be selected as needed.
  • the eccentric mechanism 2 is hydraulically driven by the eccentric mechanism 2, and in one specific example thereof, includes a "C" type eccentric sleeve that is sleeved on the power input shaft 1.
  • a slot for the eccentric plate 21 is provided on the circumference of the power input shaft 1, so that the eccentric plate 21 can follow the rotation of the power input shaft 1, so that the pressing plate 4 can follow the rotation of the power input shaft 1.
  • the chamber 23 includes two portions, which are respectively disposed on both sides of the piston 22, and the power input shaft 1 is provided with a liquid inlet hole, and the liquid inlet hole is connected to the chamber 23 through the passage 24.
  • the eccentric position of the eccentric plate 21 is adjusted by controlling the pressure difference between the two chambers 23, thereby
  • the eccentric position of the urging plate 4 mounted on the eccentric plate 21 is adjusted in accordance with the actual load.
  • the liquid can be used with various commonly used liquids such as hydraulic oil, and the pressure of the liquid can be precisely adjusted by a computer.
  • the eccentric mechanism 2 can also be implemented by other similar structures, and the eccentric position adjustment of the pressing plate 4 can be mainly completed.
  • the eccentric mechanism 2 pushes the push plate 4 to work between two extreme eccentric positions: when the eccentricity is zero, the drive plate 5, the push plate 4 and the power input shaft 1 are concentric, so that the push plate 4 and the drive No torque is transmitted between the discs 5, that is, the mechanical shifting assembly does not work; when there is a load ⁇ on the turbine output shaft 12, the eccentric mechanism 2 starts to move, pushing the pushing disc 4 to move, and the driving disc 5 is eccentrically generated.
  • the maximum transmission torque can reach the maximum eccentric position of the pushing plate 4 and the driving plate 5, in the process, the transmission torque is gradually reduced, the transmission speed ratio is gradually increased, and the function of quick start is achieved.
  • the hydraulic shifting assembly includes a pump impeller 6 fixedly coupled to the power input shaft 1, and a turbine 7 fixedly coupled to the drive disc 5.
  • a transmission medium (such as a transmission fluid) that transmits power is interposed between the impeller 6 and the turbine 7; and a turbine output shaft 12 is provided to the turbine 7.
  • the turbine 7 and the drive plate 5 are integrally connected by the turbine inner sleeve 10, so that the turbine 7 can be rotated by the drive plate 5.
  • the integral portion of the turbine 7 and the drive plate 5 is mounted on the power input shaft 1 through bearings.
  • the side of the turbine 7 remote from the drive plate 5 forms a housing enclosing the pump wheel 6 therein, the end of which forms a turbine output shaft 12.
  • the turbine output shaft 12 is connected to the power input shaft 1 via bearings.
  • the pump impeller 6 is fixedly coupled to the power input shaft 1 and rotates with the power input shaft 1 and is disposed in the casing of the turbine 7.
  • the casing of the turbine 7, the inner bushing 10 of the turbine, the bearing and the like form a sealed chamber, and the transmission liquid (for example, hydraulic oil) that transmits power is filled in the chamber, and the pipeline can be opened on the power input shaft 1 Adjust the pressure of the transmission fluid to function as a variable speed drive.
  • a guide wheel 8 is further disposed between the turbine 7 and the pump impeller 6, and the guide wheel 8 is rotatably mounted on the turbine inner sleeve 10 via a one-way clutch 9 or a bearing.
  • a lockup clutch 11 is provided between the power input shaft 1 and the turbine output shaft 12.
  • the lockup clutch 11 includes a lock piece axially movable to be mounted at the end of the power input shaft 1, and a housing suction member at the turbine 7. When the rotation speed of the turbine 7 reaches a certain value, the lock piece is moved by the transmission liquid, and is sucked with the suction member, so that the power input shaft 1 directly drives the turbine 7 to rotate, that is, the power input shaft 1 is directly output through the turbine output shaft 12. Power, the turning efficiency is the highest.
  • the main torque transmission is transmitted to the drive disc 5 via the pusher disc 4 via the slider assembly; since the drive disc 5 has a very large torque ratio at a small speed (at least one larger than the torque converter) The order of magnitude), therefore, the turbine 7 rigidly coupled to the drive plate 5 will quickly accelerate. Since the mechanical shifting assembly has a high working efficiency at a small speed ratio, the energy of the prime mover is saved, and the mechanical hydraulic continuously variable transmission is not easily heated. At this stage, the pump impeller 6 also rotates with the power input shaft 1, and the generated hydraulic force also has an auxiliary pushing effect on the turbine 7. However, the main power of the rotating power of the turbine 7 is driven by the driving disc 5.
  • the mechanical hydraulic continuously variable transmission combines the advantages of small sinusoidal continuously variable transmission with large torque ratio, large torque ratio, high efficiency, and high torque ratio of hydraulic torque converter, the advantages of both are complementary.
  • the organic combination of sex becomes a continuously variable transmission that can be efficiently transmitted under various operating conditions.
  • FIG. 3 it is a specific embodiment of a mechanical hydraulic continuously variable transmission applied to a vehicle (especially an automobile), which includes a power input shaft 1 connected to a vehicle engine, and is sequentially mounted on the power input shaft 1 A mechanical shifting assembly and a hydraulic shifting assembly, which are disposed in the outer casing, and a gear shifting assembly driven by the hydraulic shifting assembly.
  • the structural form of the mechanical shifting assembly and the hydraulic shifting assembly is the same as that of the previous embodiment, and therefore is not described.
  • the gear shifting assembly includes a sun gear 15 fixedly coupled to the turbine output shaft 12, a planetary gear meshing with the sun gear 15, an internal spur 17 meshing with the planetary gear, a planet carrier 16 for planetary gear mounting, and a turbine A clutch 13 outside the output shaft 12 and a brake 14 disposed inside the casing.
  • the clutch 13 and the brake 14 control the relationship between the carrier 16 and the sun gear 15 to control the operation of the internal gums 17.
  • Internal gear ⁇ 17 There is a power take-off shaft 18 that extends out of the outer casing.
  • the power transmission line of the vehicle is in the forward speed D, and the power input shaft 1 drives the driving disk 5 and the pump wheel 6 to rotate by the mechanical shifting assembly and the hydraulic shifting assembly, as described in the previous embodiment;
  • the clutch 13 is operated, the carrier 16 is connected to the sun gear, and the turbine output shaft 12 drives the sun gear 15 to rotate, thereby driving the planetary gears on the carrier 16 to rotate, and driving the output shaft of the gears to rotate forward, thereby realizing the advancement of the vehicle.
  • the power transmission line of the vehicle is in the reverse gear R, and the power input shaft 1 drives the drive plate 5 and the pump wheel 6 to rotate by the mechanical shifting assembly and the hydraulic shifting assembly, as described in the previous embodiment;
  • the brake 14 is actuated, so that the carrier 16 is fixedly connected to the outer casing of the transmission, and the turbine output shaft 12 drives the planetary gear to rotate through the sun gear, thereby driving the gear output shaft to rotate in the reverse direction to realize reverse driving.
  • Fig. 6 it is the power transmission route of the vehicle in the parking range P, and the control system of the vehicle controls the mechanical transmission component to be in an inoperative state, that is, the control pressing plate 4 is concentric with the driving plate 5.
  • the power input shaft 1 drives the pump wheel 6 to rotate by the hydraulic shifting assembly, as described in the previous embodiment.
  • the clutch 13 and the brake 14 act in the same manner, so that the sun gear 15 and the carrier 16 are fixedly connected to the outer casing of the transmission.
  • the gear output shaft is fixed and stops.
  • the vehicle is in the power transmission route of the neutral position N, and the control system of the vehicle controls the mechanical shifting assembly to be in an inoperative state, that is, the control pressing plate 4 is concentric with the driving plate 5.
  • the power input shaft 1 drives the pump wheel 6 to rotate by the hydraulic shifting assembly, as described in the previous embodiment.
  • the clutch 13 and the brake 14 are in an inoperative state, so that the sun gear 15 drives the carrier 16 and the planetary gear.
  • the idling free state causes the gingival output shaft to be in a free state, achieving a neutral position.
  • the shifting of the vehicle is done by mechanical shifting components and hydraulic shifting components, while the vehicle is moving forward, reversing, Parking, neutral, etc. are realized by a set of planetary gears, a clutch 13, and a brake 14.
  • the structure of the automatic shifting system consisting of a classic Simpson gear train or a Ravine brain gear train and a torque converter is simple. many. Moreover, it has the advantages of good starting acceleration performance, stepless speed change without shifting under various working conditions, high work efficiency, fuel saving and low manufacturing cost.

Description

说明书 机械液力无级变速器和方法、 及车辆机械液力无级变速器 技术领域
[1] 本发明涉及无级变速装置， 更具体地说， 涉及一种机械液力无级变速器和机械 液力无级变速方法、 以及用于车辆中的机械液力无级变速器。
背景技术
[2] 液力变矩器具有良好的自适应性和无级变速变矩功能， 对传动系统有缓冲和减 振作用， 没有机械磨损、 可靠性高、 使用寿命长， 在各种车辆、 工程机械、 建 筑机械等机械领域得到广泛应用。
[3] 但是， 液力变矩器存在变矩能力和传动效率的矛盾， 很多情况下启动慢， 输出 转矩不能满足要求。 在变矩能力较大、 小变速比吋传动效率很低， 设备发热需 增加冷却系统， 使系统结构复杂、 体积重量大。
[4] 当前汽车上使用的变速器有很多种， 如手档变速器、 钢带式无级变速器、 液力 自动变速器等等， 其中最多使用的是液力自动变速器。 液力自动变速器是由液 力变矩器和行星齿轮变速器或平行轴式齿轮变速器组成。 液力变矩器能在一定 范围内自动地无级地改变转矩比， 但其变矩系数不够大， 在小转速比吋传动效 率很低， 同吋存在变矩能力和传动效率的矛盾， 因此需要和齿轮变速器配合使 用。 但齿轮变速器换档吋既损失效率又损失速度， 而且为配合换档要增加不少 离合器、 制动器和控制机构等， 使变速器重量重、 结构复杂和体积过大等不足
[5] 正弦无级变速器是一种全新原理的无级变速器， 可以实现零启动、 无级变速， 启动力矩非常大。 在小转速比吋转矩比非常大， 工作效率很高， 结构简单、 体 积小、 重量轻。 正弦无级变速器在中国实用新型专利第 92105836.5号 《滑块离合 偏心式无级变速器》 、 200410091908.4 《摆动式滑块无级变速器》 、 2005100341 24.2 《滚道单向离合轮及使用该滚道单向离合轮的变速器》 、 200510035453.9 《 带平衡的变速器》 、 200510036495.4 《自动无级变速器》 200420094921.0 《一种自动变速装置》 、 200520062848.3 《自动无级变速器》 、 200520067825.1 《偏心式变速器离合盘的滑块组件》 、 200620013327.3 《人力车用自适应无级变 速器及带有该变速器的人力车》 等多件专利中已经公开， 并有一些具体的改进 方案。 然而， 正弦无级变速器存在大转速比工作吋， 工作效率呈下降趋势的缺 点。
发明内容
[6] 本发明要解决的技术问题在于， 针对现有技术的上述液力变矩器的很多情况下 启动慢、 输出转矩不能满足要求的缺陷， 提供一种结合机械变矩和液力变矩的 优点的机械液力无级变速器和方法。
[7] 本发明要解决的另一技术问题在于， 针对现有技术的上述汽车用液力变矩器的 很多情况下启动慢、 输出转矩不能满足要求的缺陷， 提供一种结合机械变矩和 液力变矩的优点的车辆机械液力无级变速器。
[8] 本发明解决其技术问题所釆用的技术方案是： 提供一种机械液力无级变速器， 包括依次安装在动力输入轴上、 并设置在外壳内的机械变速组件以及液力变速 组件；
[9] 所述机械变速组件包括随所述动力输入轴转动的偏心机构、 可转动安装在所述 偏心机构上的推压盘、 设置在所述推压盘一侧并固定在所述外壳内侧的固定盘 、 以及设置在所述推压盘另一侧并可转动安装在所述动力输入轴上的驱动盘； 所述偏心机构根据所述驱动盘的负载调整所述推压盘与所述动力输入轴之间的 偏心量； 所述固定盘与推压盘之间、 所述推压盘与驱动盘之间设有传递动力的 滑块组件；
[10] 所述液力变速组件包括与所述动力输入轴固定连接的泵轮、 以及与所述驱动盘 固定连接的涡轮； 所述泵轮与所述涡轮之间灌有传递动力的传动介质； 所述涡 轮设有伸出所述外壳的动力输出轴。
[11] 在本发明的机械液力无级变速器中， 所述涡轮位于所述驱动盘和泵轮之间， 并 且所述涡轮通过涡轮内轴套与所述驱动盘固定连接。
[12] 在本发明的机械液力无级变速器中， 所述涡轮与泵轮之间设有导轮； 所述导轮 通过单向离合器或者轴承安装在所述涡轮内轴套上。
[13] 在本发明的机械液力无级变速器中， 所述动力输入轴和涡轮输出轴之间设有锁 止离合器。
[14] 在本发明的机械液力无级变速器中， 所述推压盘通过轴承安装在所述偏心机构 上， 所述涡轮内轴套通过轴承安装在所述动力输入轴上； 所述偏心机构为液力 推动偏心机构；
[15] 所述偏心机构的偏心量为零吋， 所述驱动盘、 推压盘与所述动力输入轴同心； 当所述偏心机构在所述涡轮输出轴带有负载吋产生偏心量， 所述推压盘与所述 驱动盘产生偏心。
[16] 在本发明的机械液力无级变速器中， 包括与所述车辆发动机连接的动力输入轴 、 依次安装在所述动力输入轴上并设在外壳内的机械变速组件和液力变速组件 、 以及由所述液力变速组件驱动的齿轮变速组件；
[17] 所述机械变速组件包括随所述动力输入轴转动的偏心机构、 可转动安装在所述 偏心机构上的推压盘、 设置在所述推压盘一侧并固定在所述外壳内侧的固定盘 、 以及设置在所述推压盘另一侧并可转动安装在所述动力输入轴上的驱动盘； 所述偏心机构根据所述驱动盘的负载调整所述推压盘与所述动力输入轴之间的 偏心量； 所述固定盘与推压盘之间、 所述推压盘与驱动盘之间设有传递动力的 滑块组件；
[18] 所述液力变速组件包括与所述动力输入轴固定连接的泵轮、 以及与所述驱动盘 固定连接的涡轮； 所述泵轮与所述涡轮之间灌有传递动力的传动介质； 所述涡 轮设有涡轮输出轴；
[19] 所述齿轮变速组件包括与所述涡轮输出轴固定连接的太阳轮、 与所述太阳轮啮 合的行星齿轮、 与所述行星齿轮啮合的内齿圏、 供所述行星齿轮安装的行星架 、 设置在所述涡轮输出轴外侧的离合器、 以及设置在所述外壳内侧的制动器， 所述离合器和制动器控制所述行星架， 所述内齿圏具有伸出所述外壳的动力输 出轴。
[20] 在本发明的机械液力无级变速器中， 所述涡轮位于所述驱动盘和泵轮之间， 并 且所述涡轮通过涡轮内轴套与所述驱动盘固定连接。
[21] 在本发明的机械液力无级变速器中， 所述涡轮与泵轮之间设有导轮； 所述导轮 通过单向离合器或者轴承安装在所述涡轮内轴套上。 [22] 在本发明的机械液力无级变速器中， 所述动力输入轴和涡轮输出轴之间设有锁 止离合器；
[23] 所述推压盘通过轴承安装在所述偏心机构上， 所述涡轮内轴套通过轴承安装在 所述动力输入轴上； 所述偏心机构为液力推动偏心机构；
[24] 所述偏心机构的偏心量为零吋， 所述驱动盘、 推压盘与所述动力输入轴同心； 当所述偏心机构在所述涡轮输出轴带有负载吋产生偏心量， 所述推压盘与所述 驱动盘产生偏心。
[25] 本发明还提供一种机械液力无级变速方法， 包括以下步骤：
[26] S1 : 由动力输入轴引入原动力， 并通过涡轮输出轴带动负载；
[27] S2: 当传动比小吋， 偏心机构产生偏心， 带动推压盘产生偏心， 并由动力输入 轴带动所述推压盘偏心转动， 通过滑块组件带动驱动盘转动， 所述驱动盘带动 所述涡轮转动， 由所述涡轮输出轴输出动力； 同吋， 液力变速组件的泵轮在动 力输入轴的带动下转动， 通过传动介质推动涡轮转动， 起到辅助推动涡轮输出 轴输出动力的作用；
[28] S3： 当所述涡轮转速达到一定、 传动比达到一定吋， 所述偏心机构复位， 使得 所述推压盘与所述驱动盘之间同心， 此吋， 所述泵轮在所述动力输入轴的带动 下高速转动， 通过传动介质带动所述涡轮高速转动， 并通过所述涡轮输出轴输 出动力；
[29] S4: 当传动比继续加大， 直至泵轮与涡轮进入锁止状态， 传动效率达到最大值
[30] 实施本发明具有以下有益效果： 通过在液力变速组件的前级增加机械变速组件 ， 利用机械变速组件在小转速比吋转矩比大的优点， 快速的驱动液力变速组件 的涡轮启动， 并很快的加速转动； 并且在转速比达到一定吋， 液力变速组件的 泵轮到涡轮成为主要的动力传动路线， 从而综合了机械变速组件小转速比吋具 有大转矩比、 高效率的优点以及液力变速组件大转速比吋高效率工作的优点， 有机地结合了两者的优势， 具有在各种运行工况下都能获得高效传输的优点。 附图说明
[31] 下面将结合附图及实施例对本发明作进一步说明， 附图中： [32] 图 1是本发明机械液力无级变速器的结构示意图；
[33] 图 2是本发明机械液力无级变速器的偏心机构的结构示意图；
[34] 图 3是本发明车辆机械液力无级变速器的结构示意图；
[35] 图 4是使用本发明的车辆机械液力无级变速器的车辆处于前进档 D的动力传递路 线的示意图；
[36] 图 5是使用本发明的车辆机械液力无级变速器的车辆处于倒车档 R的动力传递路 线的示意图；
[37] 图 6是使用本发明的车辆机械液力无级变速器的车辆处于停车档 P的动力传递路 线的示意图；
[38] 图 7是使用本发明的车辆机械液力无级变速器的车辆处于空档 N的动力传递路线 的示意图。
具体实施方式
[39] 如图 1所示， 是本发明的机械液力无级变速器的实施例， 其包括依次安装在动 力输入轴 1上、 并设置在外壳内的机械变速组件以及液力变速组件。 该外壳用于 将整个变速器安装到适当的位置， 其形状及结构可根据实际要求进行设计。 该 外壳与动力输入轴 1和液力变速组件的涡轮输出轴 12之间通过轴承连接。
[40] 该机械变速组件包括随动力输入轴 1转动的偏心机构 2、 通过轴承安装在偏心机 构 2上的推压盘 4、 固定安装在外壳内侧的固定盘 3、 以及可转动安装在动力输入 轴 1上的驱动盘 5。 固定盘 3和驱动盘 5分别位于推压盘 4的两侧， 并且推压盘 4和 固定盘 3之间、 推压盘 4和驱动盘 5之间通过滑块组件连接， 传递动力。 该固定盘 3、 推压盘 4、 驱动盘 5和滑块组件的结构形式可以根据需要选用。
[41] 如图 2所示， 在本实施例中， 偏心机构 2釆用液力推动的偏心机构 2， 在其一个 具体例子中， 包括套设在动力输入轴 1上的" C"型偏心板 21、 与偏心板 21固定连 接的活塞 22、 以及设置在动力输入轴 1上的腔室 23。 对应的， 在动力输入轴 1的 圆周上开设有用于偏心板 21卡设的开槽， 从而偏心板 21可以跟随动力输入轴 1转 动， 从而推压盘 4可以跟随动力输入轴 1转动。 该腔室 23包括两部分， 分别设置 在活塞 22的两侧， 而动力输入轴 1上设有进液孔， 进液孔通过通道 24连接到腔室 23中。 通过控制两个腔室 23之间的压力差来调节偏心板 21的偏心位置， 从而可 以根据实际负载来调整安装在偏心板 21上的推压盘 4的偏心位置。 可以理解的， 液体可以釆用液压油等各种常用液体， 并且釆用液体的压力可以釆用计算机进 行精确调整。 当然， 偏心机构 2也可以釆用其他类似的结构实现， 主要完成对推 压盘 4的偏心位置调整即可。
[42] 偏心机构 2推动推压盘 4在两个极限偏心位置之间工作： 在偏心量为零吋， 驱动 盘 5、 推压盘 4和动力输入轴 1同心， 使得推压盘 4和驱动盘 5之间不产生力矩的传 递， 也就是说机械变速组件不工作； 当涡轮输出轴 12上有负载吋， 偏心机构 2开 始动作， 推动推压盘 4移动， 与驱动盘 5产生偏心而产生最大的传动力矩， 一直 可以到达推压盘 4和驱动盘 5的最大偏心位置， 在此过程中， 传动力矩逐渐减小 ， 传动转速比逐渐增大， 起到快速启动的作用。
[43] 液力变速组件包括与动力输入轴 1固定连接的泵轮 6、 以及与驱动盘 5固定连接 的涡轮 7。 泵轮 6与涡轮 7之间灌有传递动力的传动介质 （如传动液） ； 涡轮 7设 有涡轮输出轴 12。 在本实施例中， 涡轮 7与驱动盘 5之间通过涡轮内轴套 10连接 成一个整体， 从而涡轮 7可以在驱动盘 5的带动下转动。 涡轮 7与驱动盘 5形成的 整体通过轴承安装在动力输入轴 1上。 涡轮 7远离驱动盘 5的一侧形成包裹泵轮 6 于其中的壳体， 壳体的末端形成涡轮输出轴 12。 涡轮输出轴 12与动力输入轴 1之 间通过轴承连接。 泵轮 6与动力输入轴 1固定连接， 并随动力输入轴 1转动， 设置 在涡轮 7的壳体内。 涡轮 7的壳体、 涡轮内轴套 10、 轴承等形成一个密封的腔室 ， 在腔室内灌满传递动力的传动液 （例如液压油） ， 可以通过在动力输入轴 1上 开设管路， 来调整传动液的压力， 从而起到变速传动的作用。
[44] 在本实施例中， 在涡轮 7与泵轮 6之间还设有导轮 8， 该导轮 8通过单向离合器 9 或者轴承可转动的安装在涡轮内轴套 10上。 在动力输入轴 1和涡轮输出轴 12之间 设置有锁止离合器 11。 该锁止离合器 11包括可轴向移动安装在动力输入轴 1末端 的锁止片、 以及在涡轮 7壳体吸合件。 当涡轮 7的转速达到一定吋， 通过传动液 推动锁止片移动， 与吸合件吸合， 使得动力输入轴 1直接驱动涡轮 7转动， 也就 是说动力输入轴 1通过涡轮输出轴 12直接输出动力， 转动效率达到最高。
[45] 当原动机转动吋， 动力输入轴 1转动， 泵轮 6也同步转动， 涡轮 7在负载作用下 处于静止状态。 当控制机构 （例如汽车的控制系统） 控制机械液力无级变速器 开始工作吋， 此吋传动比很小， 控制机构通过液压推动偏心机构 2产生相对于动 力输入轴 1的偏心， 推压盘 4在偏心机构 2作用下开始偏心， 推压盘 4通过滑块组 件带动驱动盘 5转动， 主要的力矩传递是通过推压盘 4经由滑块组件传递到驱动 盘 5; 由于驱动盘 5在小转速比吋转矩比非常大 （至少比液力变矩器大一个数量 级） ， 因此与驱动盘 5刚性连接的涡轮 7会很快加速转动。 因机械变速组件在小 转速比吋工作效率很高， 因此既节省了原动机的能源， 又使机械液力无级变速 器不易发热。 在此阶段， 泵轮 6也会随着动力输入轴 1转动， 而产生的液力对涡 轮 7也有辅助推动的作用， 然而涡轮 7转动的动力主要的动力来之驱动盘 5的带动
[46] 随着涡轮输出轴 12的转速不断提高、 控制机构控制推压盘 4的偏心量增大， 转 矩比不断减小、 效率也不断降低， 此吋， 液力变速组件的效率不断提高。 当涡 轮转速达到一定、 动力输入轴 1与涡轮输出轴 12达到一定的转速比吋， 液力变速 组件的泵轮 6到涡轮 7成为主要的动力传递路线， 此吋， 控制机构控制动力输入 轴 1上的偏心机构 2停止工作， 推压盘 4归至零位， 不再推动驱动盘 5转动， 完全 进入到液力变速组件的工作状态。 此吋液力变速组件在高效区工作， 涡轮 7转速 进一步上升直到进入锁止状态， 转动效率达到 100%。
[47] 由于机械液力无级变速器综合了正弦无级变速器小转速比吋具有大转矩比、 高 效率的优点以及液力变矩器大转速比吋高效率工作的优点， 两者优势互补性的 有机结合成为各种运行工况下都能获得高效传输的无级变速器。
[48] 如图 3所示， 是机械液力无级变速器应用到车辆 （特别是汽车） 中的一个具体 实施例， 其包括与车辆发动机连接的动力输入轴 1、 依次安装在动力输入轴 1上 并设在外壳内的机械变速组件和液力变速组件、 以及由液力变速组件驱动的齿 轮变速组件。 其中机械变速组件和液力变速组件的结构形式与上一实施例相同 ， 故不赞述。
[49] 齿轮变速组件包括与涡轮输出轴 12固定连接的太阳轮 15、 与太阳轮 15啮合的行 星齿轮、 与行星齿轮啮合的内齿圏 17、 供行星齿轮安装的行星架 16、 设置在涡 轮输出轴 12外侧的离合器 13、 以及设置在外壳内侧的制动器 14。 该离合器 13和 制动器 14控制行星架 16与太阳轮 15的关系， 来控制内齿圏 17的动作。 内齿圏 17 具有伸出外壳的动力输出轴 18。
下表给出了车辆在各个工作档位， 离合器 13和制动器 14的配合关系。
Figure imgf000010_0001
[51] 如图 4所示， 是车辆处于前进档 D的动力传递路线， 动力输入轴 1通过机械变速 组件和液力变速组件带动驱动盘 5和泵轮 6转动， 如前一实施例描述； 此吋， 离 合器 13工作， 行星架 16与太阳轮连接， 涡轮输出轴 12带动太阳轮 15转动， 从而 带动行星架 16上的行星齿轮转动， 带动齿圏输出轴正向转动， 实现车辆的前进
[52] 如图 5所示， 是车辆处于倒车档 R的动力传递路线， 动力输入轴 1通过机械变速 组件和液力变速组件带动驱动盘 5和泵轮 6转动， 如前一实施例描述； 此吋， 制 动器 14动作， 使得行星架 16与变速器的外壳固定连接， 由涡轮输出轴 12通过太 阳轮带动行星齿轮转动， 从而带动齿圏输出轴反向转动， 实现倒车。
[53] 如图 6所示， 是车辆处于停车档 P的动力传递路线， 车辆的控制系统控制机械变 速组件处于不工作状态， 也就是说控制推压盘 4与驱动盘 5同心。 而动力输入轴 1 通过液力变速组件带动泵轮 6转动， 如前一实施例描述； 此吋， 离合器 13和制动 器 14同吋动作， 使得太阳轮 15、 行星架 16与变速器的外壳固定连接， 使得齿圏 输出轴固定不动， 实现停车。
[54] 如图 7所示， 是车辆处于空档 N的动力传递路线， 车辆的控制系统控制机械变速 组件处于不工作状态， 也就是说控制推压盘 4与驱动盘 5同心。 而动力输入轴 1通 过液力变速组件带动泵轮 6转动， 如前一实施例描述； 此吋， 离合器 13和制动器 14均处于不工作状态， 使得太阳轮 15带动行星架 16与行星轮处于空转自由状态 ， 使得齿圏输出轴也处于自由状态， 实现空档。
[55] 车辆的变速通过机械变速组件和液力变速组件来完成， 而车辆的前进、 倒车、 停车、 空档等通过一组行星齿轮、 一个离合器 13、 一个制动器 14来实现， 比经 典的辛普森式齿轮系或腊文脑式齿轮系和液力变矩器组成的自动变速系统的结 构简单得多。 而且具有启动加速性能好， 各种工作状况下无级变速不用换档， 工作效率高、 省油、 制造成本低等优点。

Claims

权利要求书
[1] 一种机械液力无级变速器， 其特征在于， 包括依次安装在动力输入轴上、 并设置在外壳内的机械变速组件以及液力变速组件；
所述机械变速组件包括随所述动力输入轴转动的偏心机构、 可转动安装在 所述偏心机构上的推压盘、 设置在所述推压盘一侧并固定在所述外壳内侧 的固定盘、 以及设置在所述推压盘另一侧并可转动安装在所述动力输入轴 上的驱动盘； 所述偏心机构根据所述驱动盘的负载调整所述推压盘与所述 动力输入轴之间的偏心量； 所述固定盘与推压盘之间、 所述推压盘与驱动 盘之间设有传递动力的滑块组件；
所述液力变速组件包括与所述动力输入轴固定连接的泵轮、 以及与所述驱 动盘固定连接的涡轮； 所述泵轮与所述涡轮之间灌有传递动力的传动介质 ； 所述涡轮设有伸出所述外壳的动力输出轴。
[2] 根据权利要求 1所述的机械液力无级变速器， 其特征在于， 所述涡轮位于所 述驱动盘和泵轮之间， 并且所述涡轮通过涡轮内轴套与所述驱动盘固定连 接。
[3] 根据权利要求 2所述的机械液力无级变速器， 其特征在于， 所述涡轮与泵轮 之间设有导轮； 所述导轮通过单向离合器或者轴承安装在所述涡轮内轴套 上。
[4] 根据权利要求 1、 2或 3所述的机械液力无级变速器， 其特征在于， 所述动力 输入轴和涡轮输出轴之间设有锁止离合器。
[5] 根据权利要求 4所述的机械液力无级变速器， 其特征在于， 所述推压盘通过 轴承安装在所述偏心机构上， 所述涡轮内轴套通过轴承安装在所述动力输 入轴上； 所述偏心机构为液力推动偏心机构；
所述偏心机构的偏心量为零吋， 所述驱动盘、 推压盘与所述动力输入轴同 心； 当所述偏心机构在所述涡轮输出轴带有负载吋产生偏心量， 所述推压 盘与所述驱动盘产生偏心。
[6] 一种车辆机械液力无级变速器， 其特征在于， 包括与所述车辆发动机连接 的动力输入轴、 依次安装在所述动力输入轴上并设在外壳内的机械变速组 件和液力变速组件、 以及由所述液力变速组件驱动的齿轮变速组件； 所述机械变速组件包括随所述动力输入轴转动的偏心机构、 可转动安装在 所述偏心机构上的推压盘、 设置在所述推压盘一侧并固定在所述外壳内侧 的固定盘、 以及设置在所述推压盘另一侧并可转动安装在所述动力输入轴 上的驱动盘； 所述偏心机构根据所述驱动盘的负载调整所述推压盘与所述 动力输入轴之间的偏心量； 所述固定盘与推压盘之间、 所述推压盘与驱动 盘之间设有传递动力的滑块组件；
所述液力变速组件包括与所述动力输入轴固定连接的泵轮、 以及与所述驱 动盘固定连接的涡轮； 所述泵轮与所述涡轮之间灌有传递动力的传动介质 ； 所述涡轮设有涡轮输出轴；
所述齿轮变速组件包括与所述涡轮输出轴固定连接的太阳轮、 与所述太阳 轮啮合的行星齿轮、 与所述行星齿轮啮合的内齿圏、 供所述行星齿轮安装 的行星架、 设置在所述涡轮输出轴外侧的离合器、 以及设置在所述外壳内 侧的制动器， 所述离合器和制动器控制所述行星架， 所述内齿圏具有伸出 所述外壳的动力输出轴。
[7] 根据权利要求 6所述的车辆机械液力无级变速器， 其特征在于， 所述涡轮位 于所述驱动盘和泵轮之间， 并且所述涡轮通过涡轮内轴套与所述驱动盘固 定连接。
[8] 根据权利要求 6所述的车辆机械液力无级变速器， 其特征在于， 所述涡轮与 泵轮之间设有导轮； 所述导轮通过单向离合器或者轴承安装在所述涡轮内 轴套上。
[9] 根据权利要求 6、 7或 8所述的车辆机械液力无级变速器， 其特征在于， 所述 动力输入轴和涡轮输出轴之间设有锁止离合器；
所述推压盘通过轴承安装在所述偏心机构上， 所述涡轮内轴套通过轴承安 装在所述动力输入轴上； 所述偏心机构为液力推动偏心机构； 所述偏心机构的偏心量为零吋， 所述驱动盘、 推压盘与所述动力输入轴同 心； 当所述偏心机构在所述涡轮输出轴带有负载吋产生偏心量， 所述推压 盘与所述驱动盘产生偏心。 一种机械液力无级变速方法， 其特征在于， 包括以下步骤：
S1 : 由动力输入轴引入原动力， 并通过涡轮输出轴带动负载；
S2: 当传动比小吋， 偏心机构产生偏心， 带动推压盘产生偏心， 并由动力 输入轴带动所述推压盘偏心转动， 通过滑块组件带动驱动盘转动， 所述驱 动盘带动所述涡轮转动， 由所述涡轮输出轴输出动力； 同吋， 液力变速组 件的泵轮在动力输入轴的带动下转动， 通过传动介质推动涡轮转动， 起到 辅助推动涡轮输出轴输出动力的作用；
S3： 当所述涡轮转速达到一定、 传动比达到一定吋， 所述偏心机构复位， 使得所述推压盘与所述驱动盘之间同心， 此吋， 所述泵轮在所述动力输入 轴的带动下高速转动， 通过传动介质带动所述涡轮高速转动， 并通过所述 涡轮输出轴输出动力；
S4: 当传动比继续加大， 直至泵轮与涡轮进入锁止状态， 传动效率达到最 大值。
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