WO2009129666A1 - A automobile hydraulic transmission and differential speed system and a variable volume gear pump - Google Patents

A automobile hydraulic transmission and differential speed system and a variable volume gear pump Download PDF

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Publication number
WO2009129666A1
WO2009129666A1 PCT/CN2008/001595 CN2008001595W WO2009129666A1 WO 2009129666 A1 WO2009129666 A1 WO 2009129666A1 CN 2008001595 W CN2008001595 W CN 2008001595W WO 2009129666 A1 WO2009129666 A1 WO 2009129666A1
Authority
WO
WIPO (PCT)
Prior art keywords
pump
gear
gears
cavity
sides
Prior art date
Application number
PCT/CN2008/001595
Other languages
French (fr)
Chinese (zh)
Inventor
冯政民
Original Assignee
Feng Zhengmin
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
Priority claimed from CNA2008100936891A external-priority patent/CN101260880A/en
Priority claimed from CNA2008100973388A external-priority patent/CN101307821A/en
Application filed by Feng Zhengmin filed Critical Feng Zhengmin
Publication of WO2009129666A1 publication Critical patent/WO2009129666A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/185—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by varying the useful pumping length of the cooperating members in the axial direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/60—Shafts
    • F04C2240/605—Shaft sleeves or details thereof
    • 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
    • F16H39/02—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motors at a distance from liquid pumps

Definitions

  • the present invention relates to an automotive transmission, differential structure, and variable cavity gear pump.
  • the work performed by an automobile engine is sequentially transmitted to a wheel through a clutch, a transmission, a transmission shaft, a differential, and then through a half shaft, and the structure is large in size and complicated in structure.
  • the differential is designed to prevent the car from turning when traveling, because the outer wheel is moved more than the inner wheel, and the outer wheel is slipped while the outer wheel is rolling, and the inner wheel is designed to slip while rolling. It is usually realized by a large number of gears, and the structure is very complicated.
  • an object of the present invention is to provide a hydraulic drive and differential mechanism that is small in size, simple in structure, and capable of steplessly adjusting output power.
  • the hydraulic vehicle transmission and differential mechanism of the present invention comprises a variable cavity gear pump and two hydraulic motors connected to the half shaft, wherein the outlet port of the variable cavity gear pump and the two hydraulic pressures The liquid inlet of the motor is connected through the pipeline, and the liquid outlet of the two hydraulic motors and the inlet of the variable cavity gear pump are connected through the pipeline to form two driving oil passages.
  • a communication pipe is disposed between the inlet and outlet ports of the hydraulic motor to form a differential lockback oil passage; and the differential lockback oil passage and the corresponding drive oil passage are disposed on the differential drive oil passage
  • variable cavity gear pump comprises a gear pump body, and the pump body is provided with two meshing bodies a pump gear, a cylindrical sleeve having a diameter corresponding to a pump gear coaxially disposed on both sides of the two pump gears, and a pump chamber is formed on the outer contour of the corresponding pump gear and the cylindrical sleeve on both sides of the pump body, each of which is One of the cylindrical sleeves on both sides of the pump gear has an arcuate groove on the outer circumferential surface of the sleeve, and two sleeves with arcuate grooves are located on opposite sides of the two pump gears;
  • the radius of the curved groove is equivalent to the radius of the pump gear, and the depth of the arc groove is equivalent to the depth of the two pump gears;
  • the pump chamber corresponding to any pump gear is provided with an extension along the axial direction of the pump gear
  • the diameter of the pump chamber extension is adapted to the sleeve, and the pump gear and the cylindrical sleeve on both sides thereof are
  • a synchronous structure for synchronizing the two pump gears is further provided in the pump chamber.
  • the above-mentioned synchronizing structure is specifically: two anti-intermeshing synchronizing gears are further disposed on the axles of the two pump gears, wherein the two synchronizing gears can maintain the meshing when the two pump gears move relative to each other. Further, the length of the meshing portion of the two synchronizing gears described above in the axial direction is greater than the length of the two pump gear meshing portions in the axial direction.
  • a synchronous cavity is disposed in the pump cavity or on the outer side of the pump cavity, and two synchronous gears are disposed in the synchronous cavity; wherein, the position axis of the synchronous cavity side on the gear wheel axis corresponding to the pump cavity extension
  • the synchronizing gear provided on the guide groove is axially movable relative to the guide groove.
  • FIG. 1 is a schematic structural view of a hydraulic vehicle transmission and differential mechanism according to the present invention.
  • 2 is a schematic structural view of an embodiment of the variable cavity gear pump of FIG. 1.
  • FIG. 3 is a structural schematic view of the pump gear and the bushing of the embodiment shown in FIG. 2 when moving to the middle of the pump chamber extension.
  • FIG. 4 is a perspective view of the bushing of FIG. 2 and its distribution in the pump chamber.
  • FIG. 5 is a schematic structural view of a second embodiment of a variable cavity gear pump according to the present invention.
  • Fig. 6 is a structural schematic view showing a pump gear of the second embodiment shown in Fig. 5 when the external force is applied to the pump chamber extension to the middle portion.
  • Fig. 7 is a structural schematic view showing the movement of a pump gear in the second embodiment shown in Fig. 5 to the "zero power output" when the external force is applied to the pump chamber extension.
  • Figure 8 is a schematic view showing the structure of a third embodiment of the variable cavity gear pump of the present invention.
  • Fig. 9 is a structural schematic view showing a pump gear of the third embodiment shown in Fig.
  • the hydraulic vehicle transmission and differential mechanism of the present invention comprises a variable cavity gear pump and two hydraulic motors connected to a half shaft, wherein the outlet port of the variable cavity gear pump and two The liquid inlet of the hydraulic motor is connected through the pipeline, and the liquid outlets of the two hydraulic motors and the inlet port of the variable cavity gear pump are connected through the pipeline to form two driving oil passages.
  • variable-cavity gear pump has the characteristics of stepless output power without overflowing or other pressure limiting valve; the variable-cavity gear pump can output the power of the engine through the pipeline to drive the hydraulic motor to output power
  • the half shaft is driven to drive the car, thereby saving a lot of space occupied by the original automobile transmission structure; and because it is a hydraulic transmission, the hydraulic oil that the two hydraulic motors are subjected to through the pipeline
  • the pressure is the same, so when turning, the outer wheel is subjected to less load than the inner wheel, so that the hydraulic motor that drives the outer wheel speeds up, which can replace the differential of the original car.
  • the space inside the vehicle body is further saved, and the overall structure is simple.
  • the direction of the liquid circulation in the variable-cavity gear pump can be changed by adjusting the rotation direction of the power input shaft of the variable-cavity gear pump or by installing an oil-way directional control valve on the drive oil passage.
  • the two hydraulic motors described above may be separate (as shown in Fig. 1), or they may be integrally formed so that the existing automobile structure does not need to be changed when installed on an existing automobile.
  • the above structure is also applicable to a four-wheel drive vehicle.
  • a communication pipe is further disposed between the inlet and outlet ports of the hydraulic motor to form a differential lockback oil passage; and the differential lockback oil passage and the corresponding
  • the oil circuit linkage switch is arranged on the driving oil circuit.
  • the driving oil circuit is turned off, the differential locking oil circuit is opened, and when the oil circuit linkage switch is turned on, the driving oil circuit is opened. , the differential lock back to the oil circuit is turned off.
  • This structure can control the rotation of any one of the driven wheels by simply controlling the oil passage of any hydraulic motor (hereinafter referred to as the drive oil passage).
  • FIG. 10 are schematic structural views of an embodiment of a variable-cavity gear pump according to the present invention, which includes a gear pump body 1, which has substantially the same working principle and structure as the existing gear pump, and is in the pump body thereof. There are two intermeshing pump gears 2, and two pump gears are coaxially arranged with a cylindrical sleeve 3 corresponding to the diameter of the pump gear, and the outer contour of the corresponding pump gear and the cylindrical sleeve on both sides of the pump body a pump chamber is formed.
  • an arcuate groove is axially provided on the outer circumferential surface of one of the cylindrical sleeves on each side of each pump gear, and the two belts are provided.
  • the sleeve with the curved groove is located on the opposite side of the two pump gears (see Fig. 3); the radius of the curved groove is equivalent to the radius of the pump gear, the depth of the curved groove and the two pump gears The depth of the joint is equivalent, so that the two pump gears do not block or collide with each other when moving relative to each other; the pump chamber corresponding to any pump gear is provided with an extension 4 along the axial direction of the pump gear to provide a displacement space of the pump gear.
  • the diameter of the pump chamber extension is adapted to the sleeve,
  • the cylindrical sleeve on both sides of the pump gear can move axially within the pump chamber and its extension portion relative to the other gear pump.
  • the length of the contact between the two pump gears can be changed (see the intersection of the two pump gears in Fig. 3), that is, the two pump gear working pump chambers are changed.
  • the volume can be adjusted to increase the output power of the gear pump and increase the service life of the mechanical power to save power output.
  • the centrifugal regulator can also be used to automatically control the oil output or oil pressure of the oil pump.
  • a synchronous structure for synchronizing the two pump gears is further disposed in the pump chamber; thus, the two pump gears can be relied upon after being disengaged.
  • the synchronous structure can still enter the meshing state at any time, so that zero power output can be achieved.
  • the thickness of the cylindrical bushing on both sides of the pump gear is greater than the thickness of the pump gear to ensure the "zero power output" when the pump cavity
  • the internal pressure liquid does not leak;
  • the axial length of the pump chamber extension is at least greater than the thickness of the pump gear to ensure sufficient displacement of the "zero power output” pump gear.
  • the above-mentioned synchronizing structure has various forms, as shown in FIG. 5 to FIG. 10, which are further provided with two intermeshing synchronizing gears 5 on the axles of the two pump gears, wherein two synchronizing gears are in two The pump gears remain engaged when moving relative to each other.
  • the above-mentioned synchronous structure can be designed outside the pump chamber (as shown in FIG. 5) as needed, or can be disposed in the pump chamber (as shown in FIG. 8).
  • 5 to 7 are schematic views of a synchronizing structure according to an embodiment of the present invention, wherein two synchronizing gears are disposed in the pump chamber, and the length of the engaging portion in the axial direction is greater than the length in the axial direction of the two pump gear meshing portions.
  • FIGS. 8 to 10 are schematic views showing the structure of another embodiment of the present invention, wherein a synchronizing cavity 6 is provided in or on one side of the pump chamber, and two synchronizing gears are disposed in the synchronizing cavity; wherein, in the pump cavity A position of one side of the synchronous cavity on the gear wheel shaft corresponding to the extending portion is axially provided with a guiding groove 6, and the synchronous gear disposed thereon can be axially moved relative to the guiding groove.
  • the two pump gears located in the synchronous cavity are not displaced, but the axle of the movable pump gear is synchronized with the guide groove through the guide groove.
  • the gear is displaced.
  • the hydraulic vehicle transmission and differential mechanism of the present invention can use the variable-cavity gear pump to output the power of the engine through the pipeline to drive the hydraulic motor to output power to the axle, thereby driving the vehicle to walk, thereby saving the original
  • the overall structure is simple and convenient to use; and because it is a hydraulic transmission, the pressure of the hydraulic oil that the two hydraulic motors are subjected to through the pipeline is uniform, and therefore, when the vehicle is turning, the outer wheel is subjected to the pressure. The pressure is greater than the pressure on the inner wheel, which speeds up the hydraulic motor driving the outer wheel, which can replace the differential of the original car and save space in the car body.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Retarders (AREA)

Abstract

The application provides an automobile hydraulic transmission and differential speed system, it includes a variable volume gear pump (10) and two hydraulic motors(11) connecting with two half shafts, an export of the gear pump(10) is connected with two imports of the hydraulic motors(11) through passages, two exports of the hydraulic motors(11) are connected with an import of the gear pump through passages, so two driving oil ways are formed.

Description

液力汽车传动、 差速机构及变腔式齿轮泵  Hydraulic vehicle transmission, differential mechanism and variable cavity gear pump
技术领域 本发明涉及一种汽车传动、 差速结构及变腔式齿轮泵。 背景技术 在现有的汽车领域里，汽车发动机所做出的功是依次通过离合器、变速器、 传动轴、差速器、然后通过半轴传递给车轮的， 这种结构体积较大， 结构复杂， 不利于汽车的小型化。 其中， 差速器是为了防止汽车转向行驶时， 由于外侧车 轮要比内侧车轮移过的距离大， 而导致外侧车轮在滚动的同时产生滑拖， 而内 侧车轮在滚动的同时产生滑转而设计的， 它通常是通过大量的齿轮的实现的， 结构非常复杂。 发明内容 为克服上述缺陷， 本发明的目的在于提供一种体积小、 结构简单、 可无级 调整输出功率液力汽车传动、 差速机构。 为达到上述目的， 本发明的液力汽车传动、 差速机构， 包括变腔式齿轮泵 和两个与半轴连接的液压马达组成， 其中， 变腔式齿轮泵的出液口与两个液压 马达的进液口通过管道相连通， 两个液压马达的出液口与变腔式齿轮泵的进液 口通过管道相连通， 形成两个驱动油路。 进一步地， 在所述的液压马达的进、 出液口之间还设置有连通管道， 形成 差速锁回油路； 在所述的差速锁回油路和其相应的驱动油路上设置有油路连动 开关， 当油路连动开关关断时， 驱动油路被关断， 差速锁回油路打开， 当油路 连动开关打开时， 驱动油路被打开， 差速锁回油路关断。 其中， 上述的变腔式齿轮泵包括齿轮泵泵体， 泵体内设有两个相互啮合的 泵齿轮， 两个泵齿轮两侧同轴设有与泵齿轮直径相当的圆柱形轴套， 泵体内对 应泵齿轮及其两侧的圆柱形轴套的外轮廓形成有泵腔， 所述的每个泵齿轮两侧 的圆柱轴套中有一个轴套的外圆周面上轴向设有弧形凹槽， 且两个带有弧形凹 槽的轴套位于两泵齿轮相反的一侧； 所述的弧形凹槽的半径与泵齿轮的半径相 当， 所述弧形凹槽的深度与两泵齿轮接合的深度相当； 任意一泵齿轮所对应的 泵腔沿泵齿轮轴向设有延伸部， 该泵腔延伸部的直径与轴套相适配， 且该泵齿 轮及其两侧的圆柱形轴套能相对另一泵齿轮在其泵腔及延伸部内作轴向移动。 进一步地， 在上述的泵腔内还设有使两个泵齿轮同步的同步结构。 其中， 上述的同步结构具体为： 在所述的两个泵齿轮的轮轴上还设有两个 相互啮合的同步齿轮，其中两个同步齿轮在两泵齿轮作相互运动时能保持啮合。 进一步地， 上述的两个同步齿轮的啮合部轴向上的长度大于两个泵齿轮啮 合部轴向上的长度。 进一步地， 在上述的泵腔内或泵腔外一侧设有同步腔， 两个同步齿轮设置 在同步腔内； 其中， 在泵腔延伸部所对应的齿轮轮轴上同步腔一侧的位置轴向 设有导向槽， 设置在其上的同步齿轮能相对导向槽做轴向移动。 采用上述结构， 利用变腔式齿轮泵无级输出功率的特点， 可将发动机输出 的动力通过管道驱动液压马达输出动力给半轴， 以驱动汽车行走， 从而能节约 原有汽车传动结构所占用大量的空间； 并且由于是液压传动， 两个液压马达通 过管道所承受的液压油的压力是一致的， 因此在转弯时， 外侧车轮所承受的负 荷要比内侧车轮所承受的负荷小， 使得驱动外侧车轮的液压马达转速加快， 从 而可替代原有汽车的差速器，能进一步地节约车体内的空间，且整体结构简单。 附图说明 图 1为本发明液力汽车传动、 差速机构的结构示意图。 图 2为图 1中变腔式齿轮泵实施例的结构示意图。 图 3为图 2所示实施例一泵齿轮及其轴套向泵腔延伸部移动至中部时的结 构示意图。 图 4为图 2所示轴套的立体图及其在泵腔内的分布示意图。 图 5为本发明变腔式齿轮泵第二实施例的结构示意图。 图 6为图 5所示第二实施例中一个泵齿轮在外力外用下向泵腔延伸部移动 至中部时的结构示意图。 图 7为图 5所示第二实施例中一个泵齿轮在外力外用下向泵腔延伸部移动 至 "零功率输出"时的结构示意图。 图 8为本发明变腔式齿轮泵第三实施例的结构示意图。 图 9为图 8所示第三实施例中一个泵齿轮在外力外用下向泵腔延伸部移动 至中部时的结构示意图。 图 10为图 8所示第三实施例中一个泵齿轮在外力外用下向泵腔延伸部移动 至 "零功率输出"时的结构示意图。 具体实施方式 下面结合附图和实施例对本发明作进一步的说明。 如图 1所示，本发明的液力汽车传动、差速机构，包括变腔式齿轮泵和两个 与半轴连接的液压马达组成， 其中， 变腔式齿轮泵的出液口与两个液压马达的 进液口通过管道相连通， 两个液压马达的出液口与变腔式齿轮泵的进液口通过 管道相连通， 形成两个驱动油路。 其中，上述的变腔式齿轮泵在不需要溢流阔或其它限压阀的情况下具有无 级输出功率的特点； 通过变腔式齿轮泵可将发动机输出的动力通过管道驱动液 压马达输出动力给半轴， 以驱动汽车行走， 从而能节约原有汽车传动结构所占 用大量的空间； 并且由于是液压传动， 两个液压马达通过管道所承受的液压油 的压力是一致的， 因此在转弯时， 外侧车轮所承受的负荷要比内侧车轮所承受 的负荷小， 从而使得驱动外侧车轮的液压马达转速加快， 从而可替代原有汽车 的差速器， 能进一步地节约车体内的空间， 且整体结构简单。 当需要调整车轮 旋转方向时， 通过调整变腔式齿轮泵动力输入轴的旋转方向或在驱动油路上加 装油路换向阀， 从而使变腔式齿轮泵内的液体循环方向改变即可。 上述的两个 液压马达可以是分体的（如图 1所示)， 也可以将其制成一体的， 这样安装在现 有汽车上时则不需改变现有汽车结构。 当然， 上述的结构也适用于四轮驱动的 汽车。 作为上述实施例地进一步改进， 在所述的液压马达的进、 出液口之间还设 置有连通管道， 形成差速锁回油路； 在所述的差速锁回油路和其相应的驱动油 路上设置有油路连动开关， 当油路连动开关关断时， 驱动油路被关断， 差速锁 回油路打开， 当油路连动开关打开时， 驱动油路被打开， 差速锁回油路关断。 这种结构可以通过简单控制任意一液压马达的油路 （下称驱动油路） 来实现控 制任意一个被驱动车轮的转动。 即当驱动油路被关断时， 差速锁回油路打开， 即可实现现有高级汽车中差速锁的功能。 图 2至图 10所示为本发明变腔式齿轮泵的实施例的结构示意图，其包括齿 轮泵泵体 1， 该泵体与现有齿轮泵的工作原理及结构基本相同， 在其泵体内设 有两个相互啮合的泵齿轮 2， 两个泵齿轮两侧同轴设有与泵齿轮直径相当的圆 柱形轴套 3， 泵体内对应泵齿轮及其两侧的圆柱形轴套的外轮廓形成有泵腔， 为了实现两泵齿轮相对的轴向移动， 在每个泵齿轮两侧的圆柱轴套中有一个轴 套的外圆周面上轴向设有弧形凹槽， 且两个带有弧形凹槽的轴套位于两泵齿轮 相反的一侧（参见图 3); 所述的弧形凹槽的半径与泵齿轮的半径相当， 所述弧 形凹槽的深度与两泵齿轮接合的深度相当， 以便于两泵齿轮在相对移动时不会 出现相互阻挡或碰撞；任意一泵齿轮所对应的泵腔沿泵齿轮轴向设有延伸部 4， 以提供泵齿轮的位移空间， 该泵腔延伸部的直径与轴套相适配， 且该泵齿轮及 其两侧的圆柱形轴套能相对另一泵齿轮在其泵腔及延伸部内作轴向移动。 使用时， 只需通过外力控制可移动泵齿轮与另一泵齿轮的相对位置， 就可 改变两泵齿轮接触的长度（见图 3两泵齿轮相交部），也即改变两泵齿轮工作泵 腔的体积，从而可实现任意调整齿轮泵的输出功率，提高机械动力的使用寿命， 以节省功率输出； 也可通过离心调节器来自动控制油泵出油量或油压。 TECHNICAL FIELD The present invention relates to an automotive transmission, differential structure, and variable cavity gear pump. BACKGROUND OF THE INVENTION In the field of existing automobiles, the work performed by an automobile engine is sequentially transmitted to a wheel through a clutch, a transmission, a transmission shaft, a differential, and then through a half shaft, and the structure is large in size and complicated in structure. Not conducive to the miniaturization of cars. Wherein, the differential is designed to prevent the car from turning when traveling, because the outer wheel is moved more than the inner wheel, and the outer wheel is slipped while the outer wheel is rolling, and the inner wheel is designed to slip while rolling. It is usually realized by a large number of gears, and the structure is very complicated. SUMMARY OF THE INVENTION In order to overcome the above drawbacks, an object of the present invention is to provide a hydraulic drive and differential mechanism that is small in size, simple in structure, and capable of steplessly adjusting output power. In order to achieve the above object, the hydraulic vehicle transmission and differential mechanism of the present invention comprises a variable cavity gear pump and two hydraulic motors connected to the half shaft, wherein the outlet port of the variable cavity gear pump and the two hydraulic pressures The liquid inlet of the motor is connected through the pipeline, and the liquid outlet of the two hydraulic motors and the inlet of the variable cavity gear pump are connected through the pipeline to form two driving oil passages. Further, a communication pipe is disposed between the inlet and outlet ports of the hydraulic motor to form a differential lockback oil passage; and the differential lockback oil passage and the corresponding drive oil passage are disposed on the differential drive oil passage When the oil circuit linkage switch is turned off, the driving oil circuit is turned off, the differential lock back oil circuit is opened, and when the oil circuit linkage switch is turned on, the driving oil circuit is opened, and the differential oil is locked back. The oil circuit is shut off. Wherein, the above variable cavity gear pump comprises a gear pump body, and the pump body is provided with two meshing bodies a pump gear, a cylindrical sleeve having a diameter corresponding to a pump gear coaxially disposed on both sides of the two pump gears, and a pump chamber is formed on the outer contour of the corresponding pump gear and the cylindrical sleeve on both sides of the pump body, each of which is One of the cylindrical sleeves on both sides of the pump gear has an arcuate groove on the outer circumferential surface of the sleeve, and two sleeves with arcuate grooves are located on opposite sides of the two pump gears; The radius of the curved groove is equivalent to the radius of the pump gear, and the depth of the arc groove is equivalent to the depth of the two pump gears; the pump chamber corresponding to any pump gear is provided with an extension along the axial direction of the pump gear The diameter of the pump chamber extension is adapted to the sleeve, and the pump gear and the cylindrical sleeve on both sides thereof are axially movable relative to the other pump gear in the pump chamber and the extension thereof. Further, a synchronous structure for synchronizing the two pump gears is further provided in the pump chamber. Wherein, the above-mentioned synchronizing structure is specifically: two anti-intermeshing synchronizing gears are further disposed on the axles of the two pump gears, wherein the two synchronizing gears can maintain the meshing when the two pump gears move relative to each other. Further, the length of the meshing portion of the two synchronizing gears described above in the axial direction is greater than the length of the two pump gear meshing portions in the axial direction. Further, a synchronous cavity is disposed in the pump cavity or on the outer side of the pump cavity, and two synchronous gears are disposed in the synchronous cavity; wherein, the position axis of the synchronous cavity side on the gear wheel axis corresponding to the pump cavity extension The synchronizing gear provided on the guide groove is axially movable relative to the guide groove. By adopting the above structure and utilizing the characteristics of the stepless output power of the variable cavity gear pump, the power outputted by the engine can be driven by the hydraulic motor of the pipeline to output the power to the half shaft to drive the vehicle to travel, thereby saving a large amount of the original automobile transmission structure. Because of the hydraulic transmission, the pressure of the hydraulic oil that the two hydraulic motors are subjected to through the pipeline is the same, so when turning, the outer wheel is subjected to less load than the inner wheel, so that the outer side is driven. The speed of the hydraulic motor of the wheel is increased, so that it can replace the differential of the original automobile, which can further save space in the vehicle body, and the overall structure is simple. BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a schematic structural view of a hydraulic vehicle transmission and differential mechanism according to the present invention. 2 is a schematic structural view of an embodiment of the variable cavity gear pump of FIG. 1. FIG. 3 is a structural schematic view of the pump gear and the bushing of the embodiment shown in FIG. 2 when moving to the middle of the pump chamber extension. 4 is a perspective view of the bushing of FIG. 2 and its distribution in the pump chamber. FIG. 5 is a schematic structural view of a second embodiment of a variable cavity gear pump according to the present invention. Fig. 6 is a structural schematic view showing a pump gear of the second embodiment shown in Fig. 5 when the external force is applied to the pump chamber extension to the middle portion. Fig. 7 is a structural schematic view showing the movement of a pump gear in the second embodiment shown in Fig. 5 to the "zero power output" when the external force is applied to the pump chamber extension. Figure 8 is a schematic view showing the structure of a third embodiment of the variable cavity gear pump of the present invention. Fig. 9 is a structural schematic view showing a pump gear of the third embodiment shown in Fig. 8 when the external force is applied to the pump chamber extension to the middle portion. Fig. 10 is a structural schematic view showing a pump gear of the third embodiment shown in Fig. 8 when the outer force is applied to the pump chamber extension to the "zero power output". DETAILED DESCRIPTION OF THE INVENTION The present invention will be further described below in conjunction with the accompanying drawings and embodiments. As shown in FIG. 1 , the hydraulic vehicle transmission and differential mechanism of the present invention comprises a variable cavity gear pump and two hydraulic motors connected to a half shaft, wherein the outlet port of the variable cavity gear pump and two The liquid inlet of the hydraulic motor is connected through the pipeline, and the liquid outlets of the two hydraulic motors and the inlet port of the variable cavity gear pump are connected through the pipeline to form two driving oil passages. Among them, the above-mentioned variable-cavity gear pump has the characteristics of stepless output power without overflowing or other pressure limiting valve; the variable-cavity gear pump can output the power of the engine through the pipeline to drive the hydraulic motor to output power The half shaft is driven to drive the car, thereby saving a lot of space occupied by the original automobile transmission structure; and because it is a hydraulic transmission, the hydraulic oil that the two hydraulic motors are subjected to through the pipeline The pressure is the same, so when turning, the outer wheel is subjected to less load than the inner wheel, so that the hydraulic motor that drives the outer wheel speeds up, which can replace the differential of the original car. The space inside the vehicle body is further saved, and the overall structure is simple. When it is necessary to adjust the direction of rotation of the wheel, the direction of the liquid circulation in the variable-cavity gear pump can be changed by adjusting the rotation direction of the power input shaft of the variable-cavity gear pump or by installing an oil-way directional control valve on the drive oil passage. The two hydraulic motors described above may be separate (as shown in Fig. 1), or they may be integrally formed so that the existing automobile structure does not need to be changed when installed on an existing automobile. Of course, the above structure is also applicable to a four-wheel drive vehicle. Further improved as the above embodiment, a communication pipe is further disposed between the inlet and outlet ports of the hydraulic motor to form a differential lockback oil passage; and the differential lockback oil passage and the corresponding The oil circuit linkage switch is arranged on the driving oil circuit. When the oil circuit linkage switch is turned off, the driving oil circuit is turned off, the differential locking oil circuit is opened, and when the oil circuit linkage switch is turned on, the driving oil circuit is opened. , the differential lock back to the oil circuit is turned off. This structure can control the rotation of any one of the driven wheels by simply controlling the oil passage of any hydraulic motor (hereinafter referred to as the drive oil passage). That is, when the driving oil passage is turned off, the differential lockback oil passage is opened, and the function of the differential lock in the existing advanced automobile can be realized. 2 to FIG. 10 are schematic structural views of an embodiment of a variable-cavity gear pump according to the present invention, which includes a gear pump body 1, which has substantially the same working principle and structure as the existing gear pump, and is in the pump body thereof. There are two intermeshing pump gears 2, and two pump gears are coaxially arranged with a cylindrical sleeve 3 corresponding to the diameter of the pump gear, and the outer contour of the corresponding pump gear and the cylindrical sleeve on both sides of the pump body a pump chamber is formed. In order to realize the relative axial movement of the two pump gears, an arcuate groove is axially provided on the outer circumferential surface of one of the cylindrical sleeves on each side of each pump gear, and the two belts are provided. The sleeve with the curved groove is located on the opposite side of the two pump gears (see Fig. 3); the radius of the curved groove is equivalent to the radius of the pump gear, the depth of the curved groove and the two pump gears The depth of the joint is equivalent, so that the two pump gears do not block or collide with each other when moving relative to each other; the pump chamber corresponding to any pump gear is provided with an extension 4 along the axial direction of the pump gear to provide a displacement space of the pump gear. The diameter of the pump chamber extension is adapted to the sleeve, The cylindrical sleeve on both sides of the pump gear and can move axially within the pump chamber and its extension portion relative to the other gear pump. In use, only by the external force to control the relative position of the movable pump gear and the other pump gear, the length of the contact between the two pump gears can be changed (see the intersection of the two pump gears in Fig. 3), that is, the two pump gear working pump chambers are changed. The volume can be adjusted to increase the output power of the gear pump and increase the service life of the mechanical power to save power output. The centrifugal regulator can also be used to automatically control the oil output or oil pressure of the oil pump.
但是， 上述的结构中， 为了保证正常运转必须保证两个泵齿轮始终保持啮 合状态， 即两个泵齿轮不能脱离啮合状态， 否则可能会导致在再次使用时无法 进入啮合状态而导致运转不正常。 作为本发明进一步地改进， 如图 5、 图 8所 示， 在所述的泵腔内还设有使两个泵齿轮同步的同步结构； 这样， 可以使两个 泵齿轮在脱离啮合状态后依靠同步结构仍能随时进入啮合状态， 从而可以实现 零功率输出。 为了能够使泵齿轮能够处于零功率输出， 也就是说两个泵齿轮处 于无啮合状态，泵齿轮两侧的圆柱形轴套的厚度大于泵齿轮的厚度，以保证 "零 功率输出"时泵腔内的压力液体不泄露； 泵腔延伸部的轴向长度至少大于泵齿 轮的厚度， 以保证 "零功率输出"泵齿轮有足够的位移空间。 上述的同步结构 的形式为多种，如图 5至图 10所示，其在所述的两个泵齿轮的轮轴上还设有两 个相互啮合的同步齿轮 5， 其中两个同步齿轮在两泵齿轮作相互运动时能保持 啮合。上述的同步结构根据需要可以设计在泵腔外（如图 5所示)，也可以设置 在泵腔内 （如图 8所示）。 图 5至图 7为本发明一实施例中同步结构的示意图， 其中， 两个同步齿轮 设置在泵腔内， 其啮合部轴向上的长度大于两个泵齿轮啮合部轴向上的长度。 图 8至图 10为本发明另一实施例的结构的示意图，其中，在所述的泵腔内 或一侧设有同步腔 6， 两个同步齿轮设置在同步腔内； 其中， 在泵腔延伸部所 对应的齿轮轮轴上同步腔一侧的位置轴向设有导向槽 6， 设置在其上的同步齿 轮能相对导向槽做轴向移动。 这样， 只需通过外力控制可移动泵齿轮相对另一 泵齿轮发生位移时， 位于同步腔内的两个泵齿轮并未发生位移， 而是可移动泵 齿轮的轮轴通过导向槽相对其上的同步齿轮发生位移。 这样， 同样可以保证两 个泵齿轮的同步。 综上所述， 本发明的液力汽车传动、 差速机构， 利用变变腔式齿轮泵可将 发动机输出的动力通过管道驱动液压马达输出动力给半轴， 以驱动汽车行走， 从而能节约原有汽车传动结构所占用大量的空间， 整体结构简单、 使用方便； 并且由于是液压传动，两个液压马达通过管道所承受的液压油的压力是一致的， 因此在转弯时， 外侧车轮所承受的压力要比内侧车轮所承受的压力大， 从而使 得驱动外侧车轮的液压马达转速加快， 从而可替代原有汽车的差速器， 能节约 车体空间。 However, in the above structure, in order to ensure normal operation, it is necessary to ensure that the two pump gears are always in the meshing state, that is, the two pump gears cannot be disengaged from the meshing state, otherwise the meshing state may not be entered during the re-use, and the operation may be abnormal. As a further improvement of the present invention, as shown in FIG. 5 and FIG. 8, a synchronous structure for synchronizing the two pump gears is further disposed in the pump chamber; thus, the two pump gears can be relied upon after being disengaged. The synchronous structure can still enter the meshing state at any time, so that zero power output can be achieved. In order to enable the pump gear to be at zero power output, that is, the two pump gears are in non-engaged state, the thickness of the cylindrical bushing on both sides of the pump gear is greater than the thickness of the pump gear to ensure the "zero power output" when the pump cavity The internal pressure liquid does not leak; the axial length of the pump chamber extension is at least greater than the thickness of the pump gear to ensure sufficient displacement of the "zero power output" pump gear. The above-mentioned synchronizing structure has various forms, as shown in FIG. 5 to FIG. 10, which are further provided with two intermeshing synchronizing gears 5 on the axles of the two pump gears, wherein two synchronizing gears are in two The pump gears remain engaged when moving relative to each other. The above-mentioned synchronous structure can be designed outside the pump chamber (as shown in FIG. 5) as needed, or can be disposed in the pump chamber (as shown in FIG. 8). 5 to 7 are schematic views of a synchronizing structure according to an embodiment of the present invention, wherein two synchronizing gears are disposed in the pump chamber, and the length of the engaging portion in the axial direction is greater than the length in the axial direction of the two pump gear meshing portions. 8 to 10 are schematic views showing the structure of another embodiment of the present invention, wherein a synchronizing cavity 6 is provided in or on one side of the pump chamber, and two synchronizing gears are disposed in the synchronizing cavity; wherein, in the pump cavity A position of one side of the synchronous cavity on the gear wheel shaft corresponding to the extending portion is axially provided with a guiding groove 6, and the synchronous gear disposed thereon can be axially moved relative to the guiding groove. In this way, when the displacement of the movable pump gear relative to the other pump gear is controlled by external force, the two pump gears located in the synchronous cavity are not displaced, but the axle of the movable pump gear is synchronized with the guide groove through the guide groove. The gear is displaced. In this way, the same can be guaranteed Synchronization of the pump gears. In summary, the hydraulic vehicle transmission and differential mechanism of the present invention can use the variable-cavity gear pump to output the power of the engine through the pipeline to drive the hydraulic motor to output power to the axle, thereby driving the vehicle to walk, thereby saving the original There is a large amount of space occupied by the automobile transmission structure, the overall structure is simple and convenient to use; and because it is a hydraulic transmission, the pressure of the hydraulic oil that the two hydraulic motors are subjected to through the pipeline is uniform, and therefore, when the vehicle is turning, the outer wheel is subjected to the pressure. The pressure is greater than the pressure on the inner wheel, which speeds up the hydraulic motor driving the outer wheel, which can replace the differential of the original car and save space in the car body.

Claims

权利要求书 Claim
1、一种液力汽车传动、差速机构， 其特征在于， 包括变腔式齿轮泵和两个 与半轴连接的液压马达组成， 其中， 变腔式齿轮泵的出液口与两个液压马达的 进液口通过管道相连通， 两个液压马达的出液口与变腔式齿轮泵的进液口通过 管道相连通， 形成两个驱动油路。 1. A hydraulic vehicle transmission and differential mechanism, comprising: a variable cavity gear pump and two hydraulic motors connected to a half shaft, wherein a fluid outlet of the variable cavity gear pump and two hydraulic pressures The liquid inlet of the motor is connected through the pipeline, and the liquid outlet of the two hydraulic motors and the inlet of the variable cavity gear pump are connected through the pipeline to form two driving oil passages.
2、如权利要求 1所述的液力汽车传动、差速机构， 其特征在于， 在所述的 液压马达的进、 出液口之间还设置有连通管道， 形成差速锁回油路； 在所述的 差速锁回油路和其相应的驱动油路上设置有油路连动开关， 当油路连动开关关 断时， 驱动油路被关断， 差速锁回油路打开， 当油路连动开关打开时， 驱动油 路被打开， 差速锁回油路关断。 2. The hydraulic vehicle transmission and differential mechanism according to claim 1, wherein a communication pipe is further disposed between the inlet and outlet ports of the hydraulic motor to form a differential lockback oil passage; An oil passage linkage switch is disposed on the differential lock return oil passage and the corresponding drive oil passage thereof. When the oil passage linkage switch is turned off, the drive oil passage is turned off, and the differential lock return oil passage is opened. When the oil circuit linkage switch is turned on, the drive oil passage is opened, and the differential lock return oil passage is closed.
3、如权利要求 1或 2所述的液力汽车传动、差速机构， 其中所述的变腔式 齿轮泵包括齿轮泵泵体， 泵体内设有两个相互啮合的泵齿轮， 两个泵齿轮两侧 同轴设有与泵齿轮直径相当的圆柱形轴套， 泵体内对应泵齿轮及其两侧的圆柱 形轴套的外轮廓形成有泵腔， 所述的每个泵齿轮两侧的圆柱轴套中有一个轴套 的外圆周面上轴向设有弧形凹槽， 且两个带有弧形凹槽的轴套位于两泵齿轮相 反的一侧； 所述的弧形凹槽的半径与泵齿轮的半径相当， 所述弧形凹槽的深度 与两泵齿轮接合的深度相当； 任意一泵齿轮所对应的泵腔沿泵齿轮轴向设有延 伸部， 该泵腔延伸部的直径与轴套相适配， 且该泵齿轮及其两侧的圆柱形轴套 能相对另一泵齿轮在其泵腔及延伸部内作轴向移动。 3. The hydraulic vehicle transmission and differential mechanism according to claim 1 or 2, wherein the variable cavity gear pump comprises a gear pump body, and the pump body is provided with two pump gears that mesh with each other, two pumps A cylindrical sleeve corresponding to the diameter of the pump gear is coaxially disposed on both sides of the gear, and a pump chamber is formed on the outer contour of the corresponding pump gear and the cylindrical sleeve on both sides of the pump body, and each pump gear is arranged on both sides of the pump gear An outer circumferential surface of one of the cylindrical sleeves is axially provided with an arcuate groove, and two sleeves with arcuate grooves are located on opposite sides of the two pump gears; the curved groove The radius of the pump is equal to the radius of the pump gear, and the depth of the arc groove is equivalent to the depth of the two pump gears; the pump chamber corresponding to any pump gear is provided with an extension along the axial direction of the pump gear, and the pump cavity extension The diameter of the sleeve is adapted to the sleeve, and the pump gear and the cylindrical sleeve on both sides thereof are axially movable relative to the other pump gear in its pump chamber and extension.
4、如权利要求 3所述的液力汽车传动、差速机构， 其特征在于， 在所述的 泵腔内还设有使两个泵齿轮同步的同步结构;泵齿轮两侧的圆柱形轴套的厚度 大于泵齿轮的厚度； 泵腔延伸部的轴向长度至少大于泵齿轮的厚度。 4. The hydraulic vehicle transmission and differential mechanism according to claim 3, wherein a synchronous structure for synchronizing the two pump gears is provided in the pump chamber; a cylindrical shaft on both sides of the pump gear The thickness of the sleeve is greater than the thickness of the pump gear; the axial length of the pump chamber extension is at least greater than the thickness of the pump gear.
5、如权利要求 4所述的液力汽车传动、差速机构， 其特征在于， 所述的同 步结构具体为：在所述的两个泵齿轮的轮轴上还设有两个相互啮合的同步齿轮， 其中两个同步齿轮在两泵齿轮作相互运动时能保持啮合。 The hydraulic vehicle transmission and differential mechanism according to claim 4, wherein the synchronization structure is specifically: two mutually meshing synchronizations are provided on the axles of the two pump gears. gear, Two of the synchronizing gears remain engaged when the two pump gears move relative to each other.
6、如权利要求 5所述的液力汽车传动、差速机构， 其特征在于， 所述的两 个同步齿轮的啮合部轴向上的长度大于两个泵齿轮啮合部轴向上的长度。 The hydraulic vehicle transmission and differential mechanism according to claim 5, wherein the length of the meshing portion of the two synchronizing gears in the axial direction is greater than the length of the two pump gear meshing portions in the axial direction.
7、 如权利要求 5所述的液力汽车传动、差速机构， 其特征在于， 在所述的 泵腔内或泵腔外一侧设有同步腔， 两个同步齿轮设置在同步腔内； 其中， 在泵 腔延伸部所对应的齿轮轮轴上同步腔一侧的位置轴向设有导向槽， 设置在其上 的同步齿轮能相对导向槽做轴向移动。 The hydraulic vehicle transmission and differential mechanism according to claim 5, wherein a synchronous cavity is disposed in the pump cavity or on an outer side of the pump cavity, and two synchronous gears are disposed in the synchronous cavity; Wherein, a guiding groove is axially disposed at a position on the side of the synchronous cavity on the gear wheel shaft corresponding to the extension of the pump chamber, and the synchronous gear disposed thereon can be axially moved relative to the guiding groove.
8、一种变腔式齿轮泵,其特征在于:包括齿轮泵泵体，泵体内设有两个相互 啮合的泵齿轮， 两个泵齿轮两侧同轴设有与泵齿轮直径相当的圆柱形轴套， 泵 体内对应泵齿轮及其两侧的圆柱形轴套的外轮廓形成有泵腔， 所述的每个泵齿 轮两侧的圆柱轴套中有一个轴套的外圆周面上轴向设有弧形凹槽， 且两个带有 弧形凹槽的轴套位于两泵齿轮相反的一侧； 所述的弧形凹槽的半径与泵齿轮的 半径相当， 所述弧形凹槽的深度与两泵齿轮接合的深度相当； 任意一泵齿轮所 对应的泵腔沿泵齿轮轴向设有延伸部， 该泵腔延伸部的直径与轴套相适配， 且 该泵齿轮及其两侧的圆柱形轴套能相对另一泵齿轮在其泵腔及延伸部内作轴向 移动。 8. A variable cavity gear pump, comprising: a gear pump body, wherein the pump body is provided with two pump gears meshing with each other, and the two pump gears are coaxially arranged on both sides with a cylindrical diameter corresponding to the pump gear diameter. a bushing, a pump chamber is formed on the outer contour of the corresponding pump gear and the cylindrical sleeve on both sides of the pump body, and the cylindrical sleeve on each side of the pump gear has an axial direction on the outer circumferential surface of the sleeve An arcuate groove is provided, and two bushings with arcuate grooves are located on opposite sides of the two pump gears; the radius of the arcuate groove is equal to the radius of the pump gear, the arcuate groove The depth of the pump is equivalent to the depth of the two pump gears; the pump chamber corresponding to any pump gear is provided with an extension along the axial direction of the pump gear, the diameter of the pump chamber extension is matched with the sleeve, and the pump gear and The cylindrical bushings on both sides are axially movable relative to the other pump gear in its pumping chamber and extension.
9、如权利要求 8所述的变腔式齿轮泵， 其特征在于， 在所述的泵腔内还设 有使两个泵齿轮同步的同步结构;泵齿轮两侧的圆柱形轴套的厚度大于泵齿轮 的厚度； 泵腔延伸部的轴向长度至少大于泵齿轮的厚度。 The variable cavity gear pump according to claim 8, wherein a synchronous structure for synchronizing the two pump gears is provided in the pump chamber; a thickness of the cylindrical sleeve on both sides of the pump gear Greater than the thickness of the pump gear; the axial length of the pump chamber extension is at least greater than the thickness of the pump gear.
10、 如权利要求 9所述的变腔式齿轮泵， 其特征在于， 所述的同步结构具 体为： 在所述的两个泵齿轮的轮轴上还设有两个相互啮合的同步齿轮， 其中两 个同步齿轮在两泵齿轮作相互运动时能保持啮合。 The variable-cavity gear pump according to claim 9, wherein the synchronizing structure is specifically: two intermeshing synchronizing gears are further disposed on the axles of the two pump gears, wherein The two synchronizing gears remain engaged when the two pump gears move relative to each other.
PCT/CN2008/001595 2008-04-21 2008-09-09 A automobile hydraulic transmission and differential speed system and a variable volume gear pump WO2009129666A1 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
CNA2008100936891A CN101260880A (en) 2008-04-21 2008-04-21 Cavity-variable type gear pump
CN200810093689.1 2008-04-21
CN200810097338.8 2008-05-13
CNA2008100973388A CN101307821A (en) 2008-05-13 2008-05-13 Hydraulic automobile transmission differential mechanism

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EP1130262A2 (en) * 2000-03-02 2001-09-05 Volkswagen Aktiengesellschaft Gear pump with flow capacity changing sliding unit
WO2006125873A1 (en) * 2005-05-27 2006-11-30 Volvo Compact Equipment Sas Hydraulic circuit for a public works vehicle and vehicle comprising one such circuit

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WO1993015338A1 (en) * 1992-02-04 1993-08-05 Thomas William Wielkopolski Continuously-variable hydromechanical parallel-type transmission device
DE19825667A1 (en) * 1998-06-09 1999-12-23 Bosch Gmbh Robert Hydraulic pump with reduced variation in revolutions
EP1130262A2 (en) * 2000-03-02 2001-09-05 Volkswagen Aktiengesellschaft Gear pump with flow capacity changing sliding unit
WO2006125873A1 (en) * 2005-05-27 2006-11-30 Volvo Compact Equipment Sas Hydraulic circuit for a public works vehicle and vehicle comprising one such circuit

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CN111765233A (en) * 2020-08-04 2020-10-13 邦语(上海）汽车技术有限公司 Hydraulic differential speed device
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