WO2019242370A1 - 一种无级变速器 - Google Patents
一种无级变速器 Download PDFInfo
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- WO2019242370A1 WO2019242370A1 PCT/CN2019/080439 CN2019080439W WO2019242370A1 WO 2019242370 A1 WO2019242370 A1 WO 2019242370A1 CN 2019080439 W CN2019080439 W CN 2019080439W WO 2019242370 A1 WO2019242370 A1 WO 2019242370A1
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- pump
- motor
- displacement
- variable
- variable displacement
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Classifications
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- 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
- F16H39/00—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution
- F16H39/04—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit
- F16H39/42—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit pump and motor being of different types
Definitions
- the invention relates to the field of mechanical variable speed transmission, in particular to a continuously variable transmission, in particular to the field of vehicle continuously variable transmission.
- the vehicle transmission has been pursuing a more perfect continuously variable transmission.
- the ideal transmission can match the load of the vehicle and the dynamic characteristics of the engine in real time and continuously.
- the main forms of continuously variable transmissions on vehicles are belt-type (or chain-type) continuously variable transmissions CVT and roller-turntable continuous infinite transmissions IVT.
- Belt (or chain) CVT has the advantages of continuously adjustable speed ratio, good smoothness, small and simple structure, and the disadvantage is that it requires high production technology and is difficult to transmit large torque;
- roller-to-disk continuously variable transmission IVT It consists of a disc and a roller, with a simple structure, but the energy loss caused by the friction between the disc and the roller is large, the temperature rises, and the product reliability is low.
- the traveling systems are composed of separate hydraulic pumps and hydraulic motors, and the system structure is complex, the cost is high, and the efficiency is low.
- the technical problem to be solved by the present invention is to provide a continuously variable transmission composed of a pump and a motor, and realize continuous continuously variable transmission between input and output power by adjusting the output displacement of the pump or the volume displacement of the output cavity of the motor. , Can achieve high speed, high efficiency output, and has the advantages of simple structure and reliable work.
- a continuously variable transmission includes a pump and a motor.
- the pump is a fixed displacement or variable displacement pump.
- the motor is a fixed displacement or variable displacement motor. At least one of the pump and the motor It is a variable displacement structure; the high-pressure input port of the motor communicates with the high-pressure output port of the pump, the low-pressure input port of the pump communicates with the low-pressure output port of the motor, the inner rotor of the pump is the power input, and the outer rotor of the pump For power output, the outer rotor of the pump and the inner rotor of the motor are rigidly connected or rigidly integrated.
- the rigid connection structure refers to a structure that is directly rigidly connected between the pump and the motor, or a structure that is connected through an overrunning clutch, or a structure that is connected through a rigid transmission mechanism.
- the working medium of the pump and motor is liquid, gas or gas-liquid mixture.
- the pump is a fixed displacement vane pump and the motor is a variable displacement vane motor
- the fixed displacement vane pump is disposed on the inner ring of the variable displacement vane motor
- the outer rotor and variable displacement of the fixed displacement vane pump The inner rotor of the variable-blade motor is a rigid integrated structure to form a common rotor.
- the stator of the variable-displacement vane motor is moved in the radial direction by the eccentric adjustment mechanism, thereby changing the fluid input volume of the variable-displacement motor.
- the motor is a variable displacement motor
- the fixed displacement pump and the variable displacement motor are axially arranged, the outer rotor of the fixed displacement pump and the inner of the variable displacement motor
- the rotors are rigidly connected by a spline structure.
- the high-pressure input port of the variable displacement motor communicates with the high-pressure output port of the fixed-displacement pump through a high-pressure channel.
- the low-pressure input port of the fixed-displacement pump and the low-pressure output port of the variable displacement motor Connected through low-pressure channels.
- the rigid transmission mechanism connection includes a rigid gear transmission connection or a rigid pulley transmission connection.
- variable displacement plunger motor When the fixed displacement pump is used as the pump and the variable displacement plunger motor is used as the motor, a rigid gear transmission connection is provided between the outer rotor of the fixed displacement pump and the output shaft of the variable displacement plunger motor.
- the invention has the advantages of continuous stepless speed change and a wide range of speed ratios
- the stepless speed change efficiency of the present invention is high.
- the efficiency is close to 100%;
- the invention can achieve high speed output, that is, the synchronization of output speed and input speed;
- the present invention infers the input and output torque through the pressure of liquid, gas, or gas-liquid mixture, which can achieve precise control of the gear ratio and can more conveniently implement various control strategies;
- the present invention can realize reverse gear control: changing the high and low pressure ports of the pump and the motor changes the rotation direction of the output;
- the speed of the invention is agile. Changing the displacement means changing the speed ratio.
- the main component pumps and motors of the present invention are traditional mature technologies and have high reliability.
- FIG. 1 is a schematic structural diagram of a continuously variable transmission composed of a fixed displacement pump and a variable displacement motor.
- FIG. 2 is a full map between the parameters of the present invention and the efficiency ⁇ of the continuously variable transmission, where " “" Indicates the linear change curve between the displacement V1 of the pump and the efficiency ⁇ of the continuously variable transmission, “ “” Indicates the linear change curve between the displacement V2 of the motor and the efficiency ⁇ of the continuously variable transmission, “ “” Represents the linear change curve between the speed n1 of the rotor in the pump and the efficiency ⁇ of the continuously variable transmission, “ “Indicates the linear change curve between the speed n1 of the outer rotor of the pump and the efficiency ⁇ of the continuously variable transmission,” “” Represents the linear change curve between the efficiency ⁇ 1 of the pump and the efficiency ⁇ of the continuously variable transmission, “ “” Represents the linear change curve between the efficiency ⁇ 2 of the motor and the efficiency ⁇ of the continuously variable transmission, “ “” Represents a linear change curve between the efficiency ⁇ 3 of the hydraulic transmission system and the efficiency ⁇ of the continuously variable transmission.
- FIG. 3 is a schematic diagram of a radial cross-sectional structure of a preferred embodiment of the present invention.
- FIG. 4 is an oil circuit connection diagram of a pump and a motor in Embodiment 1 of the present invention.
- FIG. 5 is a schematic view of an axial cross-sectional structure of Embodiment 1 of the present invention.
- FIG. 6 is a schematic structural diagram of Embodiment 2 of the present invention.
- FIG. 7 is a schematic structural diagram of Embodiment 3 of the present invention.
- FIG. 8 is a schematic structural diagram of Embodiment 4 of the present invention.
- a continuously variable transmission includes a fixed displacement pump 1 and a variable displacement motor 2.
- the fixed displacement pump 1 is a double-blade fixed displacement pump
- the variable displacement motor 2 is a single-vane variable displacement motor.
- the double-blade fixed displacement pump is mainly composed of an inner rotor 11, a common rotor 14, and a cavity 13.
- the position of the circle center of the double-blade fixed displacement pump 1 relative to the casing 32 is fixed;
- the single-blade variable displacement motor is mainly composed of a public The rotor 14, the stator 22, and the cavity 29 are composed.
- the stator 22 of the single-blade variable displacement motor can be moved in the radial direction by the eccentric adjustment mechanism 3, thereby changing the displacement V2 of the single-blade variable displacement motor.
- the inner rotor 11 of the double-blade fixed displacement pump is power input, and the common rotor 14 is power output.
- the low-pressure chamber 16 of the double-blade fixed-displacement pump is in communication with the low-pressure chamber 24 of the single-blade variable-displacement motor.
- the high-pressure chamber 15 of the double-blade fixed-displacement pump is in communication with the high-pressure chamber 23 of the single-blade variable-displacement motor 2.
- a continuously variable transmission includes a fixed displacement pump 1 and a variable displacement motor 2, 11 is an inner rotor of the fixed displacement pump 1, 12 is an outer rotor of the variable displacement motor 2, and 21 is a variable displacement
- the inner rotor of the motor 2, 22 is the stator of the variable displacement motor 2, the outer rotor (point A) of the fixed displacement pump 1 and the inner rotor (point B) of the variable displacement motor 2 are rigidly connected or integrated with a rigid structure;
- the working medium of the fixed pump and the motor is an oil medium, the power direction of the inner rotor 11 of the fixed displacement pump 1 is clockwise, and the direction of the force of the high pressure oil of the variable displacement motor 2 acting on the inner rotor 21 is clockwise.
- n1 / n2 1 + V2 / V1 (1)
- the input power of the displacement pump 1 is P0
- the power of the fixed displacement pump 1 acting on its outer rotor 22 is P1
- the power of the variable displacement motor 2 is P2
- the rotation torque of the fixed displacement pump 1 is T0
- the torque of the variable displacement motor 2 is T1.
- T2 T0 + T1 (4)
- T2 / T0 1 + V2 / V1 (5).
- variable displacement motor 2 When the variable displacement motor 2 continuously changes its displacement V2, it continuously changes the input and output speed ratio n1 / n2, and at the same time continuously changes the output torque and input torque ratio T2 / T0.
- a continuously variable transmission includes a fixed displacement pump 1 and a variable displacement motor 2.
- the fixed displacement pump 1 is a double-blade fixed-volume liquid pump
- the variable displacement motor 2 is a single-action variable-blade motor.
- the double-blade quantitative liquid pump and single-action variable-blade motor are axially arranged, 3 is an eccentric adjustment mechanism, 18 is a low-pressure inlet of the double-blade quantitative liquid pump, 19 is a high-pressure outlet of the double-blade quantitative liquid pump, and 25 is a motor High-pressure liquid input port, 26 is the low-pressure liquid output port of the motor, 12 is the outer rotor of the double-blade fixed-volume liquid pump, 21 is the inner rotor of the single-action variable-blade motor, 27 is the spline sleeve connecting the motor and the pump, and 17 is the pump
- the spline shaft connected to the motor 37 is a high-pressure rotary seal ring, 38 is a high-pressure passage of the housing 32, 39 is a low-pressure passage of the housing 32, 41 is a power input shaft, and 42 is a power output shaft.
- the double vane quantitative liquid pump and the single-acting variable vane motor are axially arranged. They are rigidly connected by a spline shaft 17 and a spline sleeve 27.
- the high pressure of the double vane quantitative liquid pump The outlet 19 is connected to one end of the high-pressure passage 38 through a high-pressure rotary seal ring 37.
- the high-pressure liquid input port 25 of the single-acting variable vane motor is in communication with the other end of the high-pressure passage 38.
- the low-pressure liquid output port 26 of the double-blade quantitative liquid pump is communicated.
- the action mechanism and variable speed principle of the double-blade fixed-volume liquid pump and the single-action variable-blade motor are the same as those described in the best embodiment.
- a continuously variable transmission includes a variable displacement pump 5 and a variable displacement motor 2.
- the outer rotor (point A) of the variable displacement pump 5 is rigidly connected to the inner rotor (point B) of the variable displacement motor 2.
- 51 is the inner rotor of the variable displacement pump
- 52 is the outer rotor of the variable displacement pump
- 21 is the inner rotor of the variable displacement motor
- 22 is the stator of the variable displacement motor
- the stator 22 of the variable displacement motor is connected to the housing
- the power input of the transmission is added to the inner rotor 51 of the variable displacement pump 5, and the outer rotor 52 of the variable displacement pump 5 outputs power.
- the power direction of the inner rotor 51 of the variable displacement pump is set to be clockwise, and the direction of the acting force of the high pressure oil input by the variable displacement motor 2 on the inner rotor 21 is clockwise.
- V1 and V2 are both variable, a wider range of speed ratio adjustment can be formed.
- variable displacement pump 5 the action mechanism and shifting principle of the variable displacement pump 5 and the variable displacement motor 2 are the same as the principle description in the best embodiment.
- a continuously variable transmission includes a fixed displacement pump 1 and a variable displacement motor 2.
- the outer rotor (point A) of the fixed displacement pump 1 is rigidly connected to the inner rotor (point B) of the variable displacement motor 2.
- 11 is the inner rotor of the fixed displacement pump 1
- 12 is the outer rotor of the fixed displacement pump 1
- 21 is the inner rotor of the variable displacement motor 2
- 22 is the stator of the variable displacement motor 2
- 44 is the overrunning clutch
- the stator of the variable displacement motor 2 is connected to the housing, the power input of the transmission is added to the inner rotor 11 of the fixed displacement pump 1, and the outer rotor 12 of the fixed displacement pump 1 outputs the power of the transmission.
- the power direction of the inner rotor 11 of the fixed displacement pump 1 is set to be clockwise, and the force direction of the high-pressure oil input by the variable displacement motor 2 to the inner rotor 21 is set to be clockwise.
- the displacement value of V2 is also close to zero.
- the shut-off valve 43 is closed.
- the working chamber of the variable displacement motor 2 is inside There is no high-pressure liquid, and the variable displacement motor 2 does not have the power required for rotation.
- the overrunning clutch 44 causes the outer rotor 12 of the fixed displacement pump 1 to automatically take off the inner rotor 21 of the variable displacement motor 2 during rotation.
- the transmission is a fixed-displacement pump 1.
- the rotational speed of the inner rotor 11 of the fixed-displacement pump 1 relative to its outer rotor 12 is the slip between the inner rotor 11 and its outer rotor 12 caused by the leak of the fixed-displacement pump 1.
- Differential speed, the speed n1 of the inner rotor and the speed n2 of the outer rotor are nearly equal, so the efficiency of the transmission at this time is close to 100%.
- the action mechanism and variable speed principle of the fixed displacement pump 1 and the variable displacement motor 2 are the same as the principle description in the best embodiment.
- a continuously variable transmission is driven by a liquid and includes a fixed displacement pump 1, a variable displacement motor 2 and a transmission housing 32.
- the fixed displacement pump 1 is a fixed displacement vane pump and a variable displacement motor 2 is selected.
- Variable displacement plunger motor ; fixed displacement vane pump includes outer rotor 12, inner rotor 11, high pressure outlet 19, low pressure inlet 18, low pressure cavity 16, power input shaft 41, power output shaft 42, high pressure rotary seal ring 37 and ring shape Oil passage 10;
- the variable displacement plunger motor includes a rotor 61, a swash plate 62, a high pressure inlet passage 63, a low pressure outlet 64, and an output shaft 65; and the power transmission between the pump and the motor includes a motor gear 45 and a pump gear 46.
- the outer rotor 12 of the fixed displacement vane pump can rotate freely in the transmission housing 32.
- the high pressure outlet 19 of the fixed displacement vane pump is in communication with the high pressure inlet passage 63 of the variable displacement plunger motor.
- the high pressure outlet of the fixed displacement vane pump 19 communicates with the annular oil passage 10, the annular oil passage 10 is always in communication with the high-pressure inlet passage 63 of the variable displacement plunger motor, and the annular oil passage 10 of the fixed displacement vane pump is sealed by a high pressure rotary seal ring 37, and the variable displacement plunger
- the low-pressure oil of the motor flows into the low-pressure chamber 16 of the vane pump through its low-pressure outlet 64, and the low-pressure inlet 18 of the fixed displacement vane pump communicates with the low-pressure chamber 16; the distance between the swash plate 62 of the variable displacement plunger motor and the output shaft 65 is changed.
- the angle can change the displacement of the plunger motor;
- the power output shaft 42 is rigidly connected to the outer rotor 12 of the fixed displacement vane pump, rigidly connected to the pump gear 46, the output shaft 65 is rigidly connected to the motor gear 45, and the motor gear 45 and the pump
- the gear 46 has the same number of teeth and external meshing transmission; the rotation direction of the output shaft 65 of the variable displacement plunger motor is opposite to that of the power input shaft 41 of the fixed displacement vane pump.
- the high pressure oil generated by the fixed displacement vane pump acts on the variable displacement plunger motor, causing the plunger motor to rotate and work.
- the output direction of the measuring piston motor 65 is opposite to that of the power input shaft 41. Therefore, the torque direction of the motor gear 45 acting on the pump gear 46 is the same as that of the power output shaft 42. Therefore, the output torque of the power output shaft 42 is The sum of the torque of the inner rotor 11 of the fixed displacement vane pump and the outer rotor 12 and the torque of the output shaft 65 of the variable displacement plunger motor.
- the rotation torque received by the outer rotor of the pump and the output torque of the motor are superimposed and output, the system efficiency and the output speed are greatly improved.
- the rotation torque required by the load is close to the rotation torque of the inner rotor of the pump, the The output speed of the continuously variable transmission is close to the input speed, and the efficiency of the continuously variable transmission is close to 100%, which has industrial applicability.
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Abstract
一种无级变速器，包括泵和马达，泵选用定排量泵（1）或变排量泵（5），马达选用定排量马达或变排量马达（2），且泵和马达中至少有一个是变排量结构；马达的高压输入口与泵的高压输出口连通，泵的低压输入口与马达的低压输出口连通，泵的内转子（11）为动力输入，泵的外转子（12）为动力输出，泵的外转子（12）与马达的内转子（21）为刚性连接结构或刚性一体化结构。
Description
本发明涉及机械变速传动领域，具体是一种无级变速器，尤其涉及车辆无级变速器领域。
车辆变速器一直在追求更加完美的无级变速器，理想的变速器因能实时、连续地匹配车辆的负载和发动机的动态特性。目前车辆上配备的无级变速器的主要形式为带式（或链式）无级变速器CVT及滚轮转盘式连续无限变速器IVT。带式（或链式）无级变速器CVT的优点是速比连续可调、平顺性好，结构小巧、简单，缺点是制作工艺要求高，难以传递大扭矩；滚轮转盘式连续无级变速器IVT，由圆盘和滚轮组成，结构简单，但圆盘和滚轮之间的摩擦造成的能量损失大、温升高，产品可靠性低。
在工程车辆领域，例如在挖掘机和叉车的液压驱动行走系统中，其行走系统均是由分离的液压泵和液压马达组成，系统结构复杂、成本高、效率低。
在液压驱动行走的高速工程车辆领域，其高速受限的主要原因就是液压驱动行走系统中的液压泵和液压马达的分离配合满足不了高速行走的要求。
本发明要解决的技术问题是提供一种由泵和马达组成的无级变速器，通过调整泵的输出排量或马达的输出腔体容排量来实现输入和输出动力之间的连续无级变速，能实现高转速、高效率输出，且具有结构简单、工作可靠等优点。
本发明的技术方案为：
一种无级变速器，包括泵和马达，所述的泵选用定排量泵或变排量泵，所述的马达选用定排量马达或变排量马达，且泵和马达中，至少有一个是变排量结构；所述的马达的高压输入口与泵的高压输出口连通，所述的泵的低压输入口与马达的低压输出口连通，泵的内转子为动力输入，泵的外转子为动力输出，泵的外转子与马达的内转子为刚性连接结构或刚性一体化结构。
所述的刚性连接结构指泵和马达之间直接刚性连接结构或通过超越离合器进行连接的结构或通过刚性传动机构连接的结构。
所述的泵和马达的工作介质为液体、气体或气液混合体。
当所述的泵选用定排量叶片泵、马达选用变排量叶片马达，且定排量叶片泵设置于变排量叶片马达的内圈时，其定排量叶片泵的外转子与变排量叶片马达的内转子为刚性一体化结构从而形成公共转子，变排量叶片马达的定子在偏心调整机构的作用下沿径向移动，从而改变变排量马达的进液量。
当所述的泵选用定排量泵、马达选用变排量马达，且定排量泵与变排量马达之间为轴向布置时，定排量泵的外转子与变排量马达的内转子之间通过花键结构进行刚性连接，变排量马达的高压输入口与定排量泵的高压输出口通过高压通道连通，定排量泵的低压输入口与变排量马达的低压输出口通过低压通道连通。
所述刚性传动机构连接，包括刚性齿轮传动连接或刚性带轮传动连接。
当所述的泵选用定排量叶片泵、马达选用变排量柱塞马达时，定排量泵的外转子与变排量柱塞马达的输出轴之间为刚性齿轮传动连接。
本发明的优点：
1、本发明具有连续无级变速，速比范围宽的优点；
2、本发明的无级变速效率高，当泵的内转子与泵的外转子同步时，效率接近100%；
3、本发明用于车辆上时，可省去液力耦合器或离合器，降低成本；
4、本发明能实现高转速输出，即实现输出转速与输入转速的同步；
5、本发明通过液体、气体或气液混合的压力推断输入和输出扭矩，能实现变速比的精准控制，能更方便地实现各种控制策略；
6、本发明可实现倒档操控：变换泵与马达的高低压口即改变输出的旋转方向；
7、本发明速度变化敏捷，改变排量即改变速比；
8、本发明的主要部件泵和马达均是传统的成熟技术，可靠性高。
图1是由定排量泵和变排量马达组成的无极变速器的原理结构图。
图2是本发明各参数与无极变速器效率η之间的全图，其中，“
”表示泵的排量V1与无极变速器效率η之间的线性变化曲线，“
”表示马达的排量V2与无极变速器效率η之间的线性变化曲线，“
”表示泵内转子的转速n1与无极变速器效率η之间的线性变化曲线，“
”表示泵外转子的转速n1与无极变速器效率η之间的线性变化曲线，“
”表示泵的效率η1与无极变速器效率η之间的线性变化曲线，“
”表示马达的效率η2与无极变速器效率η之间的线性变化曲线，“
”表示液压变速系统的效率η3与无极变速器效率η之间的线性变化曲线。
图3是本发明最佳实施方式的径向剖面结构示意图。
图4是本发明实施例1的泵和马达的油路连接图。
图5是本发明实施例1的轴向剖面结构示意图。
图6是本发明实施例2的原理结构图。
图7是本发明实施例3的原理结构图。
图8是本发明实施例4的原理结构图。
见图3，一种无级变速器，包括有定排量泵1和变排量马达2，定排量泵1选用双叶片固定排量泵，变排量马达2选用单叶片变排量马达，双叶片固定排量泵主要由内转子11、公共转子14和腔体13组成，双叶片固定排量泵1的圆心相对于壳体32的位置固定不变；单叶片变排量马达主要由公共转子14、定子22和腔体29组成，单叶片变排量马达的定子22能够在偏心调整机构3的作用下沿径向移动，从而改变单叶片变排量马达的排量V2。双叶片固定排量泵的内转子11为动力输入，公共转子14为动力输出。双叶片固定排量泵的低压腔16与单叶片变排量马达的低压腔24连通，双叶片固定排量泵的高压腔15与单叶片变排量马达2的高压腔23连通。
当双叶片固定排量泵的内转子11相对于公共转子14顺时针旋转时，在其高压腔15内形成高压油，这个高压油被传输到单叶片变排量马达的高压腔23内，高压腔体23内的高压油推动公共转子14相对于壳体32顺时针旋转。单叶片变排量马达旋转时低压腔24排出的低压油补充到双叶片固定排量泵的低压腔16内。
本实施例中双叶片固定排量泵和单叶片变排量马达的作用机理及变速机理说明：
（1）、结构原理：
见图1，一种无级变速器，包括定排量泵1和变排量马达2，11为定排量泵1的内转子，12为变排量马达2的外转子，21为变排量马达2的内转子，22为变排量马达2的定子，定排量泵1的外转子（A点）与变排量马达2的内转子（B点）刚性连接或一体化刚性结构；设定泵和马达的工作介质为油介质，定排量泵1内转子11的动力方向为顺时针方向，变排量马达2的高压油作用于其内转子21的作用力方向为顺时针方向。
（2）、扭矩和速比变换推演：
假设定排量泵1的内转子11相对于其外转子12旋转1周的液体排量为V1，变排量马达2的内转子21相对于其定子22旋转一周的进液量为V2, 定排量泵1的内转子12相对于定子22的转速为n1，定排量泵1的外转子12及变排量马达2的内转子21相对于定子22的转速为n2。根据闭合回路的流量相等原则，有：
V2*n2=（n1-n2）*V1，
n1/n2=1+V2/V1
（1），
假设定排量泵1的输入功率为P0，定排量泵1作用于其外转子22的功率为P1，变排量马达2的功率为P2，定排量泵1的旋转力矩为T0，变排量马达2的旋转力矩为T1，根据转矩、功率公式有：
P0=T0*n1/9550，
P1=T0*n2/9550，
P2=T1*n2/9550
（2），
由于定排量泵1的外转子12的旋转功率P1和变排量马达2的内转子12的旋转功率P2均来自于定排量泵1的输入功率P0，则：
P0=P1+P2
（3），
设定排量泵1的外转子12上形成的旋转力矩即输出扭矩为T2，则：
T2=T0+T1
（4），
根据公式（1）、（2）、（3）、（4）推导出：
T2/T0=1+V2/V1
（5）。
（3）、扭矩放大和变速的分析与说明：
由公式（5）和公式（1）可以看出，当定排量泵1的排量V1固定，输出扭矩T2和输出转速n2随变排量马达2的排量V2的变化而线性变化。
当变排量马达2连续改变其排量V2时，即连续改变了输入和输出转速比n1/n2，同时连续改变了输出力矩和输入力矩比T2/T0。
（4）、高效率输出的分析与说明：
从一般的工程概念中得知，当变排量马达2的排量趋于零时，变排量马达2的效率急剧下降，而此时定排量泵1的内转子11和外转子12近似同步，定排量泵1的效率接近100%，具体见图2。
（5）、由公式（1）n1/n2=1+V2/V1推演一个速比改变的步骤说明（假设泵为定排量叶片泵）：
1）由当前速比变换到另一个新速比，即n1/n2=C，C为待变换的新速比常数；
2）由步骤1）及公式（1）可求出V2/V1=C-1；
3）因为V1为固定值，由步骤2）可求出马达在新速比下旋转一周需要的排量V2=V1*（C-1）；
4）改变偏心机构使马达排量满足计算的新排量V2。
下面将结合本发明实施例中的附图，对本发明实施例中的技术方案进行清楚、完整地描述，显然，所描述的实施例仅仅是本发明一部分实施例，而不是全部的实施例。基于本发明中的实施例，本领域普通技术人员在没有做出创造性劳动前提下所获得的所有其他实施例，都属于本发明保护的范围。
实施例1
见图4和图5，一种无级变速器，包括有定排量泵1和变排量马达2，定排量泵1选用双叶片定量液体泵，变排量马达2选用单作用变量叶片马达，双叶片定量液体泵和单作用变量叶片马达为轴向布局结构，3为偏心调整机构，18为双叶片定量液体泵的低压入口，19为双叶片定量液体泵的高压出口，25为马达的高压液体输入口，26为马达的低压液体输出口，12为双叶片定量液体泵的外转子，21为单作用变量叶片马达的内转子，27为马达与泵的连接花键套，17为泵与马达的连接花键轴，37为高压旋转密封圈，38为壳体32的高压通道，39为壳体32的低压通道，41为动力输入轴，42为动力输出轴。
由图5可以看出，双叶片定量液体泵和单作用变量叶片马达之间为轴向布置，它们之间通过连接花键轴17和连接花键套27刚性连接，双叶片定量液体泵的高压出口19通过高压旋转密封圈37连接到高压通道38的一端，单作用变量叶片马达的高压液体输入口25与高压通道38的另一端连通，双叶片定量液体泵的低压入口18通过低压通道39与双叶片定量液体泵的低压液体输出口26连通。
本实施例中双叶片定量液体泵和单作用变量叶片马达的作用机理及变速原理与最佳实施方式中原理说明相同。
实施例2
见图6，一种无级变速器，包括变排量泵5和变排量马达2，变排量泵5的外转子（A点）与变排量马达2的内转子（B点）刚性连接，51为变排量泵的内转子，52为变排量泵的外转子，21为变排量马达的内转子，22为变排量马达的定子，变排量马达的定子22与外壳连接，变速器的动力输入加到变排量泵5的内转子51上，变排量泵5的外转子52输出动力。
设定变排量泵的内转子51的动力方向为顺时针方向，变排量马达2输入的高压油作用于其内转子21的作用力方向为顺时针方向。
假设变排量泵5的内转子51相对于其外转子52旋转1周的液体排量为V1，变排量马达2的内转子21相对于其定子22即外壳旋转一周的进液量为V2, 变排量泵5的内转子51相对于变排量马达2外壳的转速为n1，变排量泵5的外转子52相对于变排量马达2外壳的转速为n2，变排量泵5的内转子51的输入力矩为T0，变排量泵5的外转子52的旋转力矩为T2，由原理说明可知：
n1/n2=T2/T0=1+V2/V1
（6），
由于V1和V2均可变，所以可以形成更大的速比调节范围。
本实施例中变排量泵5和变排量马达2的作用机理及变速原理与最佳实施方式中原理说明相同。
实施例3
见图7，一种无级变速器，包括定排量泵1和变排量马达2，定排量泵1的外转子（A点）与变排量马达2的内转子（B点）刚性连接，11为定排量泵1的内转子，12为定排量泵1的外转子，21为变排量马达2的内转子，22为变排量马达2的定子，44为超越离合器，43为截止阀，变排量马达2的定子与外壳连接，变速器的动力输入加到定排量泵1的内转子11上，定排量泵1的外转子12输出变速器的动力。
设定定排量泵1内转子11的动力方向为顺时针方向，变排量马达2输入的高压油作用于其内转子21的作用力方向为顺时针方向。
假设定排量泵1的内转子11相对于其外转子12旋转1周的液体排量为V1，变排量马达2的内转子21相对于变排量马达2的定子即外壳旋转一周的进液量为V2, 定排量泵1的内转子12相对于变排量马达2外壳的转速为n1，定排量泵1的外转子12相对于变排量马达2外壳的转速为n2，定排量泵1的内转子11的输入力矩为T0，定排量泵1的外转子12的输出力矩为T2，由原理说明可知：
n1/n2=T2/T0=1+V2/V1
（6），
当变排量泵1外转子12的旋转力矩T2接近T0时，V2的排量值也接近于零，为提高变速器的效率，关断截止阀43，此时变排量马达2的工作腔体内没有高压液体，变排量马达2也没有旋转需要的动力，此时超越离合器44使定排量泵1的外转子12在旋转过程中自动脱掉变排量马达2的内转子21，此时的变速器就是一个定排量泵1，定排量泵1的内转子11相对于其外转子12的转速就是定排量泵1漏液产生的内转子11相对于其外转子12之间的滑差转速值，内转子的转速n1与外转子的转速n2接近相等，所以此时的变速器的效率接近100%。
本实施例中定排量泵1和变排量马达2的作用机理及变速原理与最佳实施方式中原理说明相同。
实施例4
见图8，一种无级变速器，由液体驱动，包括定排量泵1、变排量马达2和变速器壳体32，定排量泵1选用定排量叶片泵、变排量马达2选用变排量柱塞马达；定排量叶片泵包含外转子12、内转子11、高压出口19、低压入口18、低压腔16、动力输入轴41、动力输出轴42、高压旋转密封圈37和环形油路10；变排量柱塞马达包含转子61、斜盘62、高压入口通道63、低压出口64和输出轴65；泵和马达之间的动力传递包含马达齿轮45和泵齿轮46。
定排量叶片泵的外转子12可以在变速器壳体32内自由转动，定排量叶片泵的高压出口19与变排量柱塞马达的高压入口通道63连通，定排量叶片泵的高压出口19与环形油路10连通、环形油路10始终与变排量柱塞马达的高压入口通道63连通，定排量叶片泵的环形油路10靠高压旋转密封圈37密封，变排量柱塞马达的低压油通过其低压出口64流入叶片泵的低压腔16，定排量叶片泵的低压入口18与低压腔16连通；改变变排量柱塞马达的斜盘62与输出轴65之间的角度即可改变柱塞马达的排量；动力输出轴42与定排量叶片泵的外转子12刚性连接、与泵齿轮46刚性连接，输出轴65与马达齿轮45刚性连接，马达齿轮45和泵齿轮46的齿数相同、外啮合传动；变排量柱塞马达的输出轴65的旋转方向与定排量叶片泵的动力输入轴41的旋转方向相反。
实施中，当定排量叶片泵的内转子11与外转子12异步转动工作时，定排量叶片泵产生的高压油作用到变排量柱塞马达，使得柱塞马达旋转工作，由于变排量柱塞马达的输出轴65与动力输入轴41的转动方向相反，所以马达齿轮45作用到泵齿轮46上的力矩方向与动力输出轴42的力矩方向相同，所以动力输出轴42的输出力矩为定排量叶片泵的内转子11作用到外转子12的力矩与变排量柱塞马达的输出轴65的力矩之和。
本实施例中定排量叶片泵和变排量柱塞马达的作用机理及变速原理与实施例1相同。
本发明由于泵的外转子所受的旋转力矩与马达的输出力矩叠加输出，所以系统效率和输出转速均得到较大提高，当负载所需的旋转力矩与泵内转子的旋转力矩接近时，该无级变速器的输出转速接近输入转速，无级变速器的效率接近100%，具有工业实用性。
Claims (7)
- 一种无级变速器，其特征在于：包括泵和马达，所述的泵选用定排量泵或变排量泵，所述的马达选用定排量马达或变排量马达，且泵和马达中，至少有一个是变排量结构；所述的马达的高压输入口与泵的高压输出口连通，所述的泵的低压输入口与马达的低压输出口连通，泵的内转子为动力输入，泵的外转子为动力输出，泵的外转子与马达的内转子为刚性连接结构或刚性一体化结构。
- 根据权利要求1所述的一种无级变速器，其特征为：所述的刚性连接结构指泵和马达之间直接刚性连接结构或通过超越离合器进行连接的结构或通过刚性传动机构连接的结构。
- 根据权利要求1或2所述的一种无级变速器，其特征为：所述的泵和马达的工作介质为液体、气体或气液混合体。
- 根据权利要求1所述的一种无级变速器，其特征为：当所述的泵选用定排量叶片泵、马达选用变排量叶片马达，且定排量叶片泵设置于变排量叶片马达的内圈时，其定排量叶片泵的外转子与变排量叶片马达的内转子为刚性一体化结构，从而形成公共转子，变排量叶片马达的定子在偏心调整机构的作用下沿径向移动，从而改变变排量马达的进液量。
- 根据权利要求1所述的一种无级变速器，其特征为：当所述的泵选用定排量泵、马达选用变排量马达，且定排量泵与变排量马达之间为轴向布置时，定排量泵的外转子与变排量马达的内转子之间通过花键结构进行刚性连接，变排量马达的高压输入口与定排量泵的高压输出口通过高压通道连通，定排量泵的低压输入口与变排量马达的低压输出口通过低压通道连通。
- 根据权利要求2所述的一种无级变速器，其特征为：所述刚性传动机构连接，包括刚性齿轮传动连接或刚性带轮传动连接。
- 根据权利要求2所述的一种无级变速器，其特征为：当所述的泵选用定排量叶片泵、马达选用变排量柱塞马达时，定排量泵的外转子与变排量柱塞马达的输出轴之间为刚性齿轮传动连接。
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Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN85107299A (zh) * | 1985-10-07 | 1987-04-15 | 株式会社岛津制作所 | 液压变速装置 |
| CN1218155A (zh) * | 1997-11-11 | 1999-06-02 | 张玉良 | 液压偶合式传动方法 |
| WO2012087422A2 (en) * | 2010-12-20 | 2012-06-28 | Caterpillar Inc. | Multiple-variator control for split power cvt and hydrostatic transmissions |
| CN203656103U (zh) * | 2014-01-20 | 2014-06-18 | 江西科技学院 | 液压机械无级变速器 |
| CN203868275U (zh) * | 2014-04-22 | 2014-10-08 | 交城县华昌泰机械制造有限公司 | 一种液压无级变速传动机构 |
| CN105650234A (zh) * | 2016-02-06 | 2016-06-08 | 李钢 | 液压无级变速装置及其叶片泵、叶片马达 |
| CN107110319A (zh) * | 2015-01-13 | 2017-08-29 | 吉诺·米尼基耶洛 | 液压变矩器 |
| CN108730469A (zh) * | 2018-06-20 | 2018-11-02 | 合肥创源车辆控制技术有限公司 | 一种无级变速器 |
-
2018
- 2018-06-20 CN CN201810638661.5A patent/CN108730469A/zh active Pending
-
2019
- 2019-03-29 WO PCT/CN2019/080439 patent/WO2019242370A1/zh active Application Filing
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN85107299A (zh) * | 1985-10-07 | 1987-04-15 | 株式会社岛津制作所 | 液压变速装置 |
| CN1218155A (zh) * | 1997-11-11 | 1999-06-02 | 张玉良 | 液压偶合式传动方法 |
| WO2012087422A2 (en) * | 2010-12-20 | 2012-06-28 | Caterpillar Inc. | Multiple-variator control for split power cvt and hydrostatic transmissions |
| CN203656103U (zh) * | 2014-01-20 | 2014-06-18 | 江西科技学院 | 液压机械无级变速器 |
| CN203868275U (zh) * | 2014-04-22 | 2014-10-08 | 交城县华昌泰机械制造有限公司 | 一种液压无级变速传动机构 |
| CN107110319A (zh) * | 2015-01-13 | 2017-08-29 | 吉诺·米尼基耶洛 | 液压变矩器 |
| CN105650234A (zh) * | 2016-02-06 | 2016-06-08 | 李钢 | 液压无级变速装置及其叶片泵、叶片马达 |
| CN108730469A (zh) * | 2018-06-20 | 2018-11-02 | 合肥创源车辆控制技术有限公司 | 一种无级变速器 |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2022135742A1 (en) * | 2020-12-24 | 2022-06-30 | Robert Bosch Gmbh | Hydraulically actuated continuously variable transmission for an electric vehicle |
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