CN201747515U - Motor-switching variable-torque oil distribution mechanism with independent adjustment of oil suction and discharge - Google Patents
Motor-switching variable-torque oil distribution mechanism with independent adjustment of oil suction and discharge Download PDFInfo
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Abstract
本实用新型涉及配油机构,旨在提供一种吸排油独立调节的开关马达变扭矩配油机构。该配油机构包括扭矩输出机构、定量斜盘、柱塞缸筒、柱塞和柱塞腔,还包括配油阀组、配油盘组和开关变扭矩驱动机构。本实用新型有益效果通过对高速开关高压供油阀开启时间段内的柱塞位移在整个柱塞吸油行程中占空比的实时调节,输出与占空比成正比的平均扭矩,实现了开关变扭矩控制,最终直接改变了液压马达的输出扭矩;同时还具备节能、响应速度提高一个数量级、避免了过零问题和正反转切换只需改变先导阀驱动方向等优点。
The utility model relates to an oil distributing mechanism, aiming to provide a switch motor variable torque oil distributing mechanism with independent adjustment of oil suction and discharge. The oil distribution mechanism includes a torque output mechanism, a quantitative swash plate, a plunger cylinder, a plunger and a plunger cavity, and also includes an oil distribution valve group, an oil distribution plate group and a switch variable torque drive mechanism. The beneficial effect of the utility model is that by adjusting the duty ratio of the plunger displacement in the opening time period of the high-speed switch high-pressure oil supply valve in real time in the entire plunger oil suction stroke, the average torque proportional to the duty ratio is output, and the switch is realized. Torque control finally directly changes the output torque of the hydraulic motor; it also has the advantages of energy saving, an order of magnitude improvement in response speed, avoiding the zero-crossing problem, and only changing the driving direction of the pilot valve for forward and reverse switching.
Description
技术领域technical field
本实用新型涉及一种配油机构,更具体的说,是涉及一种吸排油独立调节的开关马达变扭矩配油机构。The utility model relates to an oil distribution mechanism, in particular to a switch motor variable torque oil distribution mechanism with independent adjustment of oil suction and discharge.
背景技术Background technique
柱塞液压马达是依靠压力油作用在柱塞上从而使马达输出轴活的一定转矩的,为了使柱塞能够交替与压力油口及回油口相通,必须采用配流装置,目前柱塞液压马达多采用端面配流,端面配流中所采用的主要器件就是配油盘。配油盘类似一个板式阀,由带两个弧形(“腰形”)窗口的平面贴合在开有配流孔的缸体端面,使得缸体和配油盘在垂直于马达轴的面上相对旋转,配油盘上的窗口和缸体端面开孔的相对位置按一定规律安排,以使处在供油或排油行程中的柱塞能交替与马达体上的供、排油口相通,并保证各油腔之间的隔离和密封。由于配油盘上两个弧形窗口的开角、位置均不能实时改变,因而液压马达无法通过配油机构实现变量(对输出扭矩和排量的连续调节)。到目前为止,市场上现有的变量液压马达,都只能通过实时调节液压马达另一侧的斜盘倾斜角度实现变量。而这种传统的通过调节斜盘倾斜角度的变量方式存在两个弱点:The plunger hydraulic motor relies on the pressure oil to act on the plunger so that the output shaft of the motor can move to a certain torque. In order to make the plunger communicate with the pressure oil port and the oil return port alternately, a flow distribution device must be used. At present, the plunger hydraulic Most motors use end-face flow distribution, and the main device used in end-face flow distribution is the oil distribution plate. The oil distribution plate is similar to a plate valve. A plane with two arc-shaped ("waist") windows is attached to the end face of the cylinder block with a flow distribution hole, so that the cylinder block and the oil distribution plate are on the surface perpendicular to the motor shaft. Relatively rotating, the relative positions of the window on the oil distribution plate and the opening on the end face of the cylinder body are arranged according to a certain rule, so that the plunger in the oil supply or oil discharge stroke can alternately communicate with the oil supply and oil discharge ports on the motor body , and ensure the isolation and sealing between the oil chambers. Since the opening angle and position of the two arc windows on the oil distribution plate cannot be changed in real time, the hydraulic motor cannot realize variable (continuous adjustment of output torque and displacement) through the oil distribution mechanism. So far, the existing variable hydraulic motors on the market can only realize the variable by adjusting the inclination angle of the swash plate on the other side of the hydraulic motor in real time. However, there are two weaknesses in this traditional variable way of adjusting the inclination angle of the swash plate:
1.液压马达中各柱塞产生的液压力,在驱动液压马达旋转的同时,其作用在斜盘上的力还会产生一个与斜盘倾斜角度控制方向一致的扭矩,且该扭矩随着液压马达转角的改变而变化,尽管有多个柱塞,但仍然无法完全在内部互相抵消,这部分波动的扭矩最终都加在了控制斜盘倾斜角度的变量机构上。变量机构为了克服该波动的扭矩,需要有相当大的面积来驱动,严重限制了液压马达的响应速度。1. The hydraulic pressure generated by each plunger in the hydraulic motor, while driving the hydraulic motor to rotate, the force acting on the swash plate will also generate a torque in the same direction as the control direction of the swash plate tilt angle, and the torque will follow the hydraulic pressure. The rotation angle of the motor changes. Although there are multiple plungers, they still cannot completely cancel each other out internally. This part of the fluctuating torque is finally added to the variable mechanism that controls the inclination angle of the swash plate. In order to overcome the fluctuating torque, the variable mechanism needs to have a rather large area to drive, which severely limits the response speed of the hydraulic motor.
2.液压马达切换为泵工况的临界点是排量为零的点。因此,为了切换为泵工况以回收减速、制动过程的能量,液压马达的排量调节机构必须过零点,不仅变量机构的行程大,响应速度慢,而且还很容易导致在零点附近的不稳定。2. The critical point for the hydraulic motor to switch to the pump mode is the point where the displacement is zero. Therefore, in order to switch to the pump working condition to recover the energy in the process of deceleration and braking, the displacement adjustment mechanism of the hydraulic motor must cross the zero point. Stablize.
实用新型内容Utility model content
本实用新型要解决的技术问题是,克服现有技术中的不足,提供一种吸排油独立调节的开关马达变扭矩配油机构。The technical problem to be solved by the utility model is to overcome the deficiencies in the prior art and provide a switch motor variable torque oil distribution mechanism with independent adjustment of oil suction and discharge.
为解决以上问题,本实用新型是通过如下技术方案实现:In order to solve the above problems, the utility model is realized through the following technical solutions:
本实用新型提供了一种吸排油独立调节的开关马达变扭矩配油机构,包括扭矩输出机构、定量斜盘、柱塞缸筒、柱塞和柱塞腔,还包括配油阀组、配油盘组和开关变扭矩驱动机构;The utility model provides a switch motor variable torque oil distribution mechanism with independent adjustment of oil suction and discharge, which includes a torque output mechanism, a quantitative swash plate, a plunger cylinder, a plunger and a plunger chamber, and also includes an oil distribution valve group, an oil distribution Disk group and switch variable torque drive mechanism;
所述的配油阀组由与柱塞个数相同的高速开关高压供油阀、高速开关排油-补油阀,高压供油先导阀,排油-补油先导阀和公共的配油阀体构成,每个柱塞及其相应的柱塞腔对应一个高速开关高压供油阀及与之对应的高速开关高压供油先导阀、一个高速开关排油-补油阀及与之对应的高速开关排油-补油先导阀;每个高速开关高压供油阀包括一个高速开关高压供油阀芯、一个高速开关高压供油阀弹簧、一个高速开关高压供油阀弹簧腔、一个高速开关高压供油阀轴向油口、一个高速开关高压供油阀周向油口和一个高速开关高压供油先导阀高压供油控制台阶,每个高速开关排油-补油阀包括一个高速开关排油-补油阀芯、一个高速开关排油-补油阀弹簧、一个高速开关排油-补油阀弹簧腔、一个高速开关排油-补油阀轴向油口、一个高速开关排油-补油阀周向油口和一个高速开关排油-补油先导阀排油-补油控制台阶;在每个高速开关高压供油先导阀靠近壳体侧端面与高速开关高压供油先导阀高压供油控制台阶之间,高速开关高压供油先导阀高压供油控制台阶与靠近中心侧端面之间各有一个容腔,在每个高速开关排油-补油先导阀靠近壳体侧端面与高速开关排油-补油先导阀排油-补油控制台阶之间,高速开关排油-补油先导阀排油-补油控制台阶与高速开关排油-补油先导阀靠近中心侧端面之间各有一个容腔;每个柱塞对应的高速开关高压供油阀与高速开关排油-补油阀都并排设置,高速开关高压供油阀轴向油口和高速开关排油-补油阀轴向油口均与其对应的柱塞腔连通;每个高速开关高压供油阀周向油口,均穿过高速开关高压供油先导阀高压供油控制台阶与高速开关高压供油先导阀靠近中心侧端面之间的容腔,与配油盘高压油流道连通;每个高速开关排油-补油阀周向油口,均穿过高速开关排油-补油先导阀排油-补油控制台阶与高速开关排油-补油先导阀靠近中心侧端面之间的容腔,与配油盘回油流道连通;每个高速开关高压供油阀弹簧腔均与相应的高速开关高压供油先导阀高压供油控制台阶连通,每个高速开关排油-补油阀弹簧腔均与相应的高速开关排油-补油先导阀排油-补油控制台阶连通;每个高速开关高压供油先导阀和高速开关排油-补油先导阀的两个端面(靠近壳体侧端面与靠近中心侧端面)均与泄漏油口连通,每个高速开关高压供油先导阀高压供油控制台阶与高速开关高压供油先导阀靠近中心侧的端面之间的容腔与配油盘高压油流道连通;每个高速开关排油-补油先导阀排油-补油控制台阶与高速开关排油-补油先导阀靠近中心侧端面之间的容腔与配油盘回油流道连通;每个高速开关高压供油先导阀靠近壳体侧端面与高速开关高压供油先导阀高压共供油控制台阶之间的容腔均与相应的高速开关高压供油先导阀对应的柱塞腔相连,每个高速开关排油-补油先导阀靠近壳体侧端面与高速开关排油-补油先导阀排油-补油控制台阶之间的容腔均与相应的高速开关排油-补油先导阀对应的柱塞腔相连;所有高速开关高压供油先导阀位于同一截面上,所有高速开关排油-补油先导阀位于同-截面上。The oil distribution valve group is composed of a high-speed switching high-pressure oil supply valve, a high-speed switching oil discharge-fill valve, a high-pressure oil supply pilot valve, an oil discharge-fill pilot valve and a common oil distribution valve with the same number as the plunger Each plunger and its corresponding plunger cavity correspond to a high-speed switch high-pressure oil supply valve and the corresponding high-speed switch high-pressure oil supply pilot valve, a high-speed switch oil discharge-supplement valve and the corresponding high-speed oil supply valve On-off oil drain-fill oil pilot valve; each high-speed switch high-pressure oil supply valve includes a high-speed switch high-pressure oil supply valve core, a high-speed switch high-pressure oil supply valve spring, a high-speed switch high-pressure oil supply valve spring cavity, a high-speed switch high-pressure oil supply valve Oil supply valve axial oil port, a high-speed switch high-pressure oil supply valve circumferential oil port and a high-speed switch high-pressure oil supply pilot valve high-pressure oil supply console stage, each high-speed switch drain-fill valve includes a high-speed switch drain - Charge spool, a high-speed switch drain-fill valve spring, a high-speed switch drain-fill valve spring cavity, a high-speed switch drain-fill valve axial port, a high-speed switch drain-fill The circumferential oil port of the oil valve and a high-speed switch oil discharge-oil supply pilot valve oil discharge-oil supply console stage; each high-speed switch high-pressure oil supply pilot valve is close to the shell side end face and the high-speed switch high-pressure oil supply pilot valve high-pressure supply Between the oil control steps, there is a cavity between the high-speed switch high-pressure oil supply pilot valve high-pressure oil supply control steps and the end surface near the center side, and between the high-speed switch oil discharge-replenish pilot valve end surface near the housing side and the high-speed Between the stage of the switch drain-fill pilot valve oil drain-fill control console, between the high-speed switch drain-fill pilot valve drain-fill console step and the high-speed switch drain-fill pilot valve near the center side end face Each has a cavity; each plunger corresponds to a high-speed switch high-pressure oil supply valve and a high-speed switch oil drain-fill valve are arranged side by side, and a high-speed switch high-pressure oil supply valve axial oil port and a high-speed switch oil drain-fill valve The axial oil ports are connected with the corresponding plunger cavity; the circumferential oil ports of each high-speed switch high-pressure oil supply valve pass through the high-speed switch high-pressure oil supply pilot valve high-pressure oil supply console step and are close to the high-speed switch high-pressure oil supply pilot valve The cavity between the end faces of the center side communicates with the high-pressure oil passage of the oil distribution plate; the circumferential oil port of each high-speed switch oil discharge-replenishment valve passes through the high-speed switch oil discharge-replenishment pilot valve oil discharge-replenishment The cavity between the oil console step and the high-speed switch oil discharge-supplement pilot valve near the center side is connected with the oil return channel of the oil distribution plate; each high-speed switch high-pressure oil supply valve spring cavity is connected to the corresponding high-speed switch high-pressure The oil supply pilot valve is connected to the high-pressure oil supply console step, and the spring cavity of each high-speed switch oil discharge-oil replenishment valve is connected to the corresponding high-speed switch oil discharge-oil replenishment pilot valve oil discharge-oil replenishment console stage; each high-speed switch high-pressure The two end faces of the oil supply pilot valve and the high-speed switch oil discharge-fill oil pilot valve (the end face near the shell side and the end face near the center side) are connected to the leakage oil port, and each high-speed switch high-pressure oil supply pilot valve is controlled by high-pressure oil supply The cavity between the step and the end face of the high-speed switch high-pressure oil supply pilot valve near the center is connected with the high-pressure oil flow channel of the oil distribution plate; each high-speed switch drains oil-replenishes the pilot valve oil drains-fuels the control stage and the high-speed switch Drain-fill oil The cavity between the end face of the pilot valve close to the center is connected with the oil return channel of the oil distribution plate; the end face of each high-speed switch high-pressure oil supply pilot valve near the housing side is between the high-speed switch high-pressure oil supply pilot valve high-pressure common oil supply console step The cavities between them are connected with the corresponding plunger cavity of the corresponding high-speed switch high-pressure oil supply pilot valve. -The cavities between the steps of the oil charge console are connected to the corresponding plunger chambers of the corresponding high-speed switch oil drain-fill pilot valves; all the high-speed switch high-pressure oil supply pilot valves are located on the same section, and all the high-speed switch oil drain-fill The oil pilot valve is located on the same section.
所述的配油盘组用螺钉固定于所述的配油阀体位于柱塞另一侧的端面,配油盘组内部有高压油流道和回油流道;配油盘组中心的配油盘高压油流道与所述所有高速开关高压供油先导阀上的高速开关高压供油先导阀高压供油控制台阶与高速开关高压供油先导阀靠近中心侧端面之间的容腔连通,配油盘高压油流道与壳体上的高压油口连通;配油盘组中心的配油盘高压油流道外侧的环形配油盘回油流道与所述所有高速开关排油-补油先导阀上的高速开关排油-补油先导阀排油-补油控制台阶与高速开关排油-补油先导阀靠近中心侧端面之间的容腔连通,配油盘组上的环形配油盘回油流道与壳体上的回油口连通;泄漏油流道与泵本体上的泄漏油流道共用,与壳体上的泄漏油口连通;所述的配油盘组中心配油盘高压油流道与其外侧的环形配油盘回油流道之间,环形配油盘回油流道与靠近壳体侧的泄漏油流道之间分别采用高压旋转支撑组件和低压旋转支撑组件提供旋转支撑,配油盘组与后端盖之间相对转动。The oil distribution plate set is fixed on the end surface of the oil distribution valve body on the other side of the plunger with screws, and there are high-pressure oil flow channels and oil return flow channels inside the oil distribution plate set; The high-pressure oil channel of the oil pan communicates with the cavities between the high-speed switch high-pressure oil supply pilot valves on the high-speed switch high-pressure oil supply pilot valves, the high-pressure oil supply console steps and the high-speed switch high-pressure oil supply pilot valves near the center side, The high-pressure oil flow channel of the oil distribution plate is connected with the high-pressure oil port on the shell; the annular oil return flow channel of the oil distribution plate outside the high-pressure oil flow channel of the oil distribution plate in the center of the oil distribution plate group is connected with all the high-speed switches described above. The high-speed switch oil discharge-replenishment pilot valve on the oil discharge-replenishment pilot valve is connected to the cavity between the high-speed switch oil discharge-replenishment pilot valve near the center side end face, and the ring valve on the oil distribution plate group The oil return channel of the oil pan is connected with the oil return port on the casing; the leakage oil flow channel is shared with the leakage oil flow channel on the pump body and communicated with the leakage oil port on the casing; Between the high-pressure oil channel of the oil pan and the oil return channel of the annular oil distribution plate on the outer side, and between the oil return channel of the annular oil distribution plate and the leakage oil channel near the shell side, high-pressure rotary support components and low-pressure rotary support components are used respectively. The assembly provides rotational support, and the relative rotation between the oil distribution plate group and the rear end cover.
作为一种改进,所述吸排油独立调节的开关马达变扭矩配油机构,其开关变扭矩驱动机构分为高压供油驱动机构和排油-补油驱动机构,其中高压供油驱动机构由一个高速开关高压供油先导阀驱动轴承及两个高速开关高压供油先导阀驱动轴承控制阀体、两个高速开关高压供油先导阀驱动轴承控制柱塞、两个高速开关高压供油先导阀驱动轴承控制弹簧、两个高速开关高压供油先导阀驱动轴承控制弹簧压片和与弹簧对应的两个高速开关高压供油先导阀驱动轴承控制弹簧腔组成,排油-补油驱动机构由一个高速开关排油-补油先导阀驱动轴承及两个高速开关排油-补油先导阀驱动轴承控制阀体、两个高速开关排油-补油先导阀驱动轴承控制柱塞、两个高速开关排油-补油先导阀驱动轴承控制弹簧、两个高速开关排油-补油先导阀驱动轴承控制弹簧压片和与弹簧对应的两个高速开关排油-补油先导阀驱动轴承控制弹簧腔组成;高压供油驱动机构的两个控制柱塞与高速开关高压供油先导阀驱动轴承轴线垂直,与该轴承运动方向所在直线共线,与该轴承外圈相切,圆周方向均布,每个高速开关高压供油先导阀驱动轴承控制柱塞与高速开关高压供油先导阀驱动轴承外圈不接触的端面安装高速开关高压供油先导阀驱动轴承控制弹簧,高速开关高压供油先导阀驱动轴承控制弹簧的另一端面设置高速开关高压供油先导阀驱动轴承控制弹簧压片,高速开关高压供油先导阀驱动轴承控制柱塞、高速开关高压供油先导阀驱动轴承控制弹簧、高速开关高压供油先导阀驱动轴承控制弹簧压片均位于高速开关高压供油先导阀驱动轴承控制控制阀体内,其内部的高速开关高压供油先导阀驱动轴承控制弹簧腔与外部的控制油路连通,高速开关高压供油先导阀驱动轴承控制控制阀体与高速开关高压供油先导阀驱动轴承控制控制柱塞同轴,安装在控制驱动外壳上,高速开关高压供油先导阀驱动轴承内圈与其驱动的高速开关高压供油先导阀靠近壳体侧端面接触并提供旋转支撑;高速开关排油-补油驱动机构的两个高速开关排油-补油先导阀驱动轴承控制柱塞与高速开关高压供油先导阀驱动轴承轴线垂直,与该轴承运动方向所在直线共线,与该轴承外圈相切,圆周方向均布,每个高速开关排油-补油先导阀驱动轴承控制柱塞与高速开关排油-补油先导阀驱动轴承外圈不接触的端面安装高速开关排油-补油先导阀驱动轴承控制弹簧,高速开关排油-补油先导阀驱动轴承控制弹簧的另一端面设置高速开关排油-补油先导阀驱动轴承控制弹簧压片,高速开关排油-补油先导阀驱动轴承控制柱塞、高速开关排油-补油先导阀驱动轴承控制弹簧、高速开关排油-补油先导阀驱动轴承控制弹簧压片均位于高速开关排油-补油先导阀驱动轴承控制控制阀体内,其内部的弹簧腔与外部的控制油路连通,控制阀体与高速开关排油-补油先导阀驱动轴承控制柱塞同轴,安装在控制驱动外壳上,高速开关排油-补油先导阀驱动轴承内圈与其驱动的高速开关排油-补油先导阀靠近壳体侧端面接触并提供旋转支撑;高速开关高压供油先导阀驱动轴承只控制高速开关高压供油先导阀,高速开关高压供油先导阀只控制高速开关高压供油阀,高速开关排油-补油先导阀驱动轴承只控制高速开关排油-补油先导阀,高速开关排油-补油先导阀只控制高速开关排油-补油阀,如此实现了配油机构的吸、排油独立调节。As an improvement, the switch motor variable torque oil distribution mechanism with independent adjustment of oil suction and discharge, its switch variable torque drive mechanism is divided into a high-pressure oil supply drive mechanism and an oil discharge-replenishment drive mechanism, wherein the high-pressure oil supply drive mechanism consists of a High-speed switch high-pressure oil supply pilot valve drive bearing and two high-speed switch high-pressure oil supply pilot valve drive bearing control valve body, two high-speed switch high-pressure oil supply pilot valve drive bearing control plunger, two high-speed switch high-pressure oil supply pilot valve drive Bearing control spring, two high-speed switch high-pressure oil supply pilot valve drive bearing control spring pressing plate and two high-speed switch high-pressure oil supply pilot valve drive bearing control spring chamber corresponding to the spring. The oil discharge-oil supply drive mechanism consists of a high-speed Oil discharge-replenishment pilot valve drive bearing of switch and two high-speed switch oil discharge-replenishment pilot valve drive bearing control valve body, two high-speed switch oil discharge-replenishment pilot valve drive bearing control plunger, two high-speed switch rows Oil-replenishment pilot valve drive bearing control spring, two high-speed switches oil discharge-replenishment pilot valve drive bearing control spring pressure plate and two high-speed switches oil discharge-replenishment pilot valve drive bearing control spring chamber corresponding to the spring ; The two control plungers of the high-pressure oil supply drive mechanism are perpendicular to the axis of the drive bearing of the high-speed switch high-pressure oil supply pilot valve, collinear with the straight line where the bearing moves, tangent to the outer ring of the bearing, and distributed uniformly in the circumferential direction. The high-speed switch high-pressure oil supply pilot valve drive bearing control plunger is not in contact with the high-speed switch high-pressure oil supply pilot valve drive bearing. The end face is installed with the high-speed switch high-pressure oil supply pilot valve drive bearing. The other end face of the control spring is provided with a high-speed switch high-pressure oil supply pilot valve drive bearing control spring pressing piece, a high-speed switch high-pressure oil supply pilot valve drive bearing control plunger, a high-speed switch high-pressure oil supply pilot valve drive bearing control spring, a high-speed switch high-pressure supply valve The oil pilot valve drive bearing control spring pressure pieces are all located in the high-speed switch high-pressure oil supply pilot valve drive bearing control control valve body, and the internal high-speed switch high-pressure oil supply pilot valve drive bearing control spring chamber is connected with the external control oil circuit, and the high-speed switch The high-pressure oil supply pilot valve drive bearing control control valve body is coaxial with the high-speed switch high-pressure oil supply pilot valve drive bearing control control plunger, installed on the control drive shell, the high-speed switch high-pressure oil supply pilot valve drive bearing inner ring and its high-speed drive On-off high-pressure oil supply pilot valve is in contact with the end face of the housing side and provides rotational support; two high-speed on-off oil drain-fill pilot valves of the high-speed switch oil discharge-fill drive mechanism drive the bearing control plunger and high-speed switch high-pressure oil supply pilot The axis of the valve driving bearing is vertical, collinear with the straight line where the direction of motion of the bearing is, and tangent to the outer ring of the bearing, evenly distributed in the circumferential direction. - The end face of the oil supplement pilot valve drive bearing outer ring is not in contact with the high-speed oil discharge switch - the oil supply pilot valve drive bearing control spring, the high speed switch oil discharge - oil supplement pilot valve drive bearing The other end of the bearing control spring is equipped with a high-speed oil discharge switch - Oil supplement pilot valve drive bearings control spring pressure piece, high-speed switch oil discharge - Oil supplement pilot valve drive bearings The control plunger, the high-speed switch oil discharge-oil supplement pilot valve drive bearing control spring, the high-speed switch oil discharge-oil supplement pilot valve drive bearing control spring pressure piece are all located in the high-speed switch oil discharge-oil supplement pilot valve drive bearing control control valve body , the inner spring cavity is connected with the external control oil circuit, the control valve body is coaxial with the high-speed switch oil discharge-oil replenishment pilot valve drive bearing control plunger, installed on the control drive shell, the high-speed switch oil discharge-oil replenishment pilot The inner ring of the valve drive bearing is in contact with the high-speed switch oil discharge-fill pilot valve close to the end face of the shell side and provides rotational support; the drive bearing of the high-speed switch high-pressure oil supply pilot valve only controls the high-speed switch high-pressure oil supply pilot valve, and the high-speed switch high-pressure The oil supply pilot valve only controls the high-speed switch high-pressure oil supply valve, the high-speed switch oil discharge-replenishment pilot valve drive bearing only controls the high-speed switch oil discharge-replenishment pilot valve, the high-speed switch oil discharge-replenishment pilot valve only controls the high-speed switch discharge The oil-supplement valve realizes the independent adjustment of the oil suction and discharge of the oil distribution mechanism.
作为一种改进,所述配油盘组由配油盘、高压旋转支撑组件、低压旋转支撑组件和后端盖组成,与吸、排油腰形孔以吸排油分界面为中心对称分布的传统配油盘不同,配油盘内部有配油盘高压油流道和配油盘回油流道,中心圆柱状流道作为配油盘高压油流道,配油盘高压油流道外侧的环形流道作为配油盘回油流道,配油盘回油流道外壁外侧为泄露油腔;配油盘与先导阀体配合端面上中心圆型区域一侧与先导阀体高压油流道连通,另一端与配油盘高压油流道直接连通,圆形区域外侧的环形区域一侧与先导阀体回油流道连通,另一端通过4个相同均布的腰形孔与配油盘回油流道连通;高压旋转支撑组件提供配油盘高压流道与配油盘回油流道之间的密封,低压旋转支撑组件提供配油盘回油流道与泄漏油流道之间的密封,高压旋转支撑组件和低压旋转支撑组件共同提供配油盘与后端盖之间的旋转支撑。As an improvement, the oil distribution plate group is composed of an oil distribution plate, a high-pressure rotary support assembly, a low-pressure rotary support assembly and a rear end cover, and is compatible with the traditional distribution system in which the oil suction and discharge waist-shaped holes are symmetrically distributed around the oil suction and discharge interface. The oil pan is different. Inside the oil distribution pan, there are oil distribution pan high-pressure oil passages and oil distribution pan return oil passages. The central cylindrical flow passage serves as the oil distribution pan high-pressure oil passage. The oil distribution channel is used as the oil return flow channel of the oil distribution plate, and the outer wall of the oil return flow channel of the oil distribution plate is the leakage oil chamber; the side of the central circular area on the mating end surface of the oil distribution plate and the pilot valve body is connected with the high pressure oil flow channel of the pilot valve body, The other end is directly connected to the high-pressure oil channel of the oil distribution plate, one side of the annular area outside the circular area is connected to the oil return channel of the pilot valve body, and the other end is connected to the oil return channel of the oil distribution plate through four uniformly distributed waist-shaped holes. The flow channel is connected; the high-pressure rotary support assembly provides the seal between the high-pressure flow channel of the oil distribution plate and the oil return flow channel of the oil distribution plate, and the low-pressure rotary support assembly provides the seal between the oil return flow channel of the oil distribution plate and the leakage oil flow channel. The high pressure swivel support assembly and the low pressure swivel support assembly together provide swivel support between the oil distribution pan and the rear end cover.
作为一种改进,所述高速开关高压供油先导阀轴线在高速开关阀所在平面上的投影与高速开关排油-补油先导阀轴线在高速开关阀所在平面上的投影以吸排油分界线为轴线对称。As an improvement, the projection of the axis of the high-speed switch high-pressure oil supply pilot valve on the plane where the high-speed switch valve is located and the projection of the axis of the high-speed switch oil discharge-replenishment pilot valve on the plane where the high-speed switch valve is located take the oil suction and discharge boundary line as the axis symmetry.
作为一种改进,所述高速开关高压供油先导阀驱动轴承的内壁中心轴线与所述柱塞缸筒的中心轴线平行,并沿着与吸排油分界线有一小于10°夹角的方向有一个固定偏置,高速开关高压供油先导阀驱动轴承能且只能在该方向的垂直方向左右移动;高速开关排油-补油先导阀驱动轴承的内壁中心轴线与所述柱塞缸筒的中心轴线平行,并沿着与吸排油分界线有一小于10°夹角的方向有一个固定偏置,该方向与高速开关高压供油先导阀驱动轴承固定偏置方向在高速开关阀所在平面的投影关于吸排油分界面对称,高速开关排油-补油先导阀驱动轴承能且只能在该方向的垂直方向左右移动。As an improvement, the central axis of the inner wall of the driving bearing of the high-speed switch high-pressure oil supply pilot valve is parallel to the central axis of the plunger cylinder, and there is a fixed angle along the direction with an angle of less than 10° with the oil suction and discharge boundary line. Offset, the driving bearing of the high-speed switch high-pressure oil supply pilot valve can and can only move left and right in the vertical direction of the direction; Parallel, and there is a fixed offset along the direction with an included angle of less than 10° with the oil suction and discharge boundary line. This direction is related to the projection of the high-speed switch high-pressure oil supply pilot valve drive bearing fixed offset direction on the plane where the high-speed switch valve is located. The interface is symmetrical, and the high-speed switch drain-fill pilot valve drive bearing can and can only move left and right in the vertical direction of this direction.
作为一种改进,所述高速开关高压供油先导阀靠近中心侧端面,其直径比高速开关高压供油先导阀高压供油控制台阶的直径略小,该面积差给高速开关高压供油先导阀提供了一个径向的压力,使得所有的高速开关高压供油先导阀都能够压在所述的高速开关高压供油先导阀驱动轴承上。所述高速开关排油-补油先导阀靠近中心侧端面,其直径比高速开关排油-补油先导阀排油-补油控制台阶的直径小,该面积差给高速开关排油-补油先导阀提供了一个径向的压力,使得所有的高速开关排油-补油先导阀都能够压在所述的高速开关排油-补油先导阀驱动轴承上。As an improvement, the high-speed switch high-pressure oil supply pilot valve is close to the end face of the center side, and its diameter is slightly smaller than the diameter of the high-speed switch high-pressure oil supply pilot valve high-pressure oil supply console step. A radial pressure is provided so that all high-speed switch high-pressure oil supply pilot valves can be pressed on the high-speed switch high-pressure oil supply pilot valve drive bearings. The high-speed switch oil discharge-replenishment pilot valve is close to the end face of the center side, and its diameter is smaller than the diameter of the high-speed switch oil discharge-replenishment pilot valve oil discharge-replenishment console step, and this area is poor for the high-speed switch oil discharge-replenishment The pilot valve provides a radial pressure so that all the high-speed switch oil discharge-charge pilot valves can be pressed on the high-speed switch oil discharge-charge pilot valve driving bearing.
作为一种改进,所述的配油阀体在轴向被分成三片:柱塞腔分油阀体、主阀体、先导阀体;柱塞腔分油阀体、主阀体、先导阀体通过销钉刚性连接到柱塞缸筒上,配油阀体与配油盘组通过螺钉连接在一起;柱塞腔分油阀体与主阀体、主阀体与先导阀体、先导阀体与配油盘组、柱塞腔分油阀体与柱塞缸筒之间所有油口的外缘,都设有密封圈。As an improvement, the oil distribution valve body is divided into three pieces in the axial direction: the oil distribution valve body in the plunger cavity, the main valve body, and the pilot valve body; the oil distribution valve body in the plunger cavity, the main valve body, and the pilot valve body The body is rigidly connected to the plunger cylinder through pins, and the oil distribution valve body and the oil distribution plate group are connected together by screws; the plunger chamber oil distribution valve body and the main valve body, the main valve body and the pilot valve body, and the pilot valve body Sealing rings are provided on the outer edges of all oil ports between the oil distribution plate group, the plunger chamber oil distribution valve body and the plunger cylinder.
作为一种改进,所述的高速开关高压供油先导阀高压供油控制台阶与高速开关排油-补油先导阀排油-补油控制台阶的宽度均与先导阀体上相应的沉割槽宽度一致,使得先导阀能够快速响应柱塞位置的变化。As an improvement, the width of the high-speed switch high-pressure oil supply pilot valve high-pressure oil supply console step and the high-speed switch oil discharge-replenishment pilot valve oil discharge-replenishment console step are both the same as the corresponding undercut grooves on the pilot valve body. The uniform width allows the pilot valve to respond quickly to changes in plunger position.
作为一种改进,所述的高速开关高压供油先导阀驱动轴承和高速开关排油-补油先导阀驱动轴承的位移为零时,高速开关高压供油阀弹簧腔除了在排油-吸油过渡点被隔离外,其他位置均与配油盘组中心高压油流道连通,使高速开关高压供油阀保持关闭,高速开关排油-补油阀弹簧腔除了在吸油-排油过渡点被隔离外,其他位置均与柱塞腔连通,使高速开关排油-补油阀保持打开,使马达能够从配油盘组的配油盘回油流道补油。As an improvement, when the displacement of the driving bearing of the high-speed switch high-pressure oil supply pilot valve and the high-speed switch oil discharge-supplement pilot valve drive bearing is zero, the spring chamber of the high-speed switch high-pressure oil supply valve will Except for the isolated point, the other positions are connected with the high-pressure oil passage in the center of the oil distribution plate group, so that the high-speed switch high-pressure oil supply valve remains closed, and the spring chamber of the high-speed switch oil discharge-supplement valve is isolated except at the transition point of oil suction-oil discharge In addition, the other positions are all connected with the plunger cavity, so that the high-speed switch oil discharge-replenishment valve remains open, so that the motor can replenish oil from the oil distribution plate return flow channel of the oil distribution plate group.
作为一种改进,所述的高速开关高压供油先导阀驱动轴承位移为零时,高速开关高压供油先导阀的初始位移为负的高速开关高压供油先导阀驱动轴承与柱塞缸筒中心轴线之间的固定偏置;高速开关高压供油先导阀高压供油控制台阶将高速开关高压供油阀弹簧腔、高速开关高压供油先导阀靠近壳体侧端面与高速开关高压供油先导阀高压供油控制台阶之间的容腔、高速开关高压供油先导阀高压供油控制台阶与高速开关高压供油先导阀靠近中心侧端面之间的容腔互相隔断;所述的高速开关排油-补油先导阀控制轴承位移为零时,高速开关排油-补油先导阀的初始位移为两倍的高速开关排油-补油先导阀驱动轴承与柱塞缸筒中心轴线之间的固定偏置;高速开关排油-补油先导阀排油-补油控制台阶将高速开关排油-补油阀弹簧腔与柱塞腔连通,且高速开关排油-补油先导阀阀口开度为两倍的高速开关排油-补油先导阀驱动轴承与柱塞缸筒中心轴线之间的固定偏置。As an improvement, when the displacement of the driving bearing of the high-speed switching high-pressure oil supply pilot valve is zero, the initial displacement of the high-speed switching high-pressure oil supply pilot valve is negative. Fixed offset between axes; high-speed switch high-pressure oil supply pilot valve high-pressure oil supply control console step will high-speed switch high-pressure oil supply valve spring chamber, high-speed switch high-pressure oil supply pilot valve close to the side end face of the shell and high-speed switch high-pressure oil supply pilot valve The cavity between the steps of the high-pressure oil supply console, the cavity between the steps of the high-pressure oil supply pilot valve of the high-speed switch and the high-pressure oil supply pilot valve of the high-speed switch are separated from each other; - Oil charge pilot valve control bearing displacement is zero, high-speed switch oil discharge - Oil charge pilot valve initial displacement is twice the high-speed switch oil discharge - Oil charge pilot valve drive bearing and fixed between the center axis of the plunger cylinder Bias; the high-speed switch oil discharge-oil replenishment pilot valve oil discharge-oil replenishment console step connects the high-speed switch oil discharge-oil replenishment valve spring chamber with the plunger chamber, and the high-speed switch oil discharge-oil replenishment pilot valve port opening Fixed offset between drain-charge pilot valve drive bearing and plunger cylinder center axis for double high speed switch.
本实用新型中,用于柱塞液压马达吸、排油独立调节的机液先导开关变扭矩配油组件的开关变扭矩方法:In the utility model, the switch variable torque method of the hydraulic pilot switch variable torque oil distribution assembly used for independent adjustment of plunger hydraulic motor suction and oil discharge:
首先,对初始位置以及正方向定义如下:First, define the initial position and positive direction as follows:
1.取吸排油分界线上,柱塞处于柱塞杠筒最深处时为起始点,起始角度为0°;1. On the boundary line of suction, suction and discharge, the plunger is at the deepest point of the plunger barrel as the starting point, and the starting angle is 0°;
2.正对输出轴,取左旋为正,右旋为负;2. Facing the output shaft, take left-handed as positive and right-handed as negative;
3.所有的先导阀驱动轴承向右为正,向左为负;3. All pilot valve drive bearings are positive when they are to the right, and negative when they are to the left;
4.所有的先导阀芯向上运动为正,向下为负;4. The upward movement of all pilot spools is positive, and the downward movement is negative;
5.所有的先导阀位移中间值规定为阀芯的0位;5. The intermediate value of displacement of all pilot valves is defined as the 0 position of the spool;
6.坐标轴取正视输出轴,水平向右为X轴正方向,竖直向上为Y轴正方向;6. The coordinate axis is the output axis of the front view, the positive direction of the X-axis is horizontally to the right, and the positive direction of the Y-axis is vertically upward;
7.以柱塞缸筒中心为原点,驱动轴承向右、向上为正,向左、向下为负;7. Taking the center of the plunger cylinder as the origin, the driving bearing is positive when it is moving to the right and upward, and negative when it is moving to the left and downward;
该开关变扭矩方法包括以下步骤:The switch variable torque method comprises the following steps:
(1)根据对输出扭矩大小的要求,调节高速开关高压供油先导阀驱动轴承和高速开关排油-补油先导阀驱动轴承,用以改变各高速开关高压供油阀的开关时间占空比;(1) According to the requirements of the output torque, adjust the driving bearing of the high-speed switch high-pressure oil supply pilot valve and the high-speed switch oil discharge-oil supply pilot valve drive bearing to change the switching time duty ratio of each high-speed switch high-pressure oil supply valve ;
(2)控制高速开关高压供油阀的开启时间,使得位于吸油区的柱塞腔,仅在高速开关高压供油阀开启时,能够从高压油口吸油,推动相应的柱塞做功;位于吸油区的柱塞腔在高速开关供油阀关闭时,均通过与回油口相通的高速开关排油-补油阀,直接从回油口吸油,补充柱塞运动产生的空腔,但不会推动柱塞做功;与此同时,位于排油区的柱塞腔,仅在高速开关高压供油阀关闭时,能够通过与回油口相通的高速开关排油-补油阀,直接排到回油口,不阻碍柱塞运动;位于排油区的柱塞腔在高速开关排油-补油阀关闭时,均通过高压供油阀向高压油口排油,工作在泵工况,实现减速与制动,并把制动能变回成压力能;确保平均输出扭矩与高速开关高压供油阀开启时间段内柱塞的位移在整个柱塞吸油行程中的占空比成正比;(2) Control the opening time of the high-speed switch high-pressure oil supply valve so that the plunger chamber located in the oil-absorbing area can absorb oil from the high-pressure oil port and push the corresponding plunger to do work only when the high-speed switch high-pressure oil supply valve is opened; When the high-speed switch oil supply valve is closed, the plunger cavity in the zone directly sucks oil from the oil return port through the high-speed switch oil discharge-replenishment valve connected to the oil return port, and replenishes the cavity generated by the plunger movement, but will not Push the plunger to do work; at the same time, the plunger chamber located in the oil discharge area can directly discharge to the return port through the high-speed switch oil discharge-supplement valve connected to the oil return port only when the high-speed switch high-pressure oil supply valve is closed. The oil port does not hinder the movement of the plunger; the plunger chamber located in the oil discharge area discharges oil to the high-pressure oil port through the high-pressure oil supply valve when the high-speed switch oil discharge-replenishment valve is closed, and works in the pump mode to achieve deceleration and braking, and convert the braking energy back into pressure energy; ensure that the average output torque is proportional to the duty ratio of the displacement of the plunger in the entire plunger oil suction stroke during the opening period of the high-speed switch high-pressure oil supply valve;
(3)通过对高速开关高压供油阀开启时间段内柱塞的位移在整个柱塞吸、排油行程中占空比的实时调节,输出与占空比成正比的平均扭矩,实现变扭矩控制;占空比与平均扭矩之间的关系为:(3) Through the real-time adjustment of the duty ratio of the displacement of the plunger during the opening period of the high-speed switch high-pressure oil supply valve in the entire plunger suction and oil discharge stroke, the average torque proportional to the duty ratio is output to realize variable torque control; the relationship between the duty cycle and the average torque is:
T=[D1-(1-D2)]*(Dm×P×η机×η阀)T=[D 1 -(1-D 2 )]*(D m ×P× ηmachine × ηvalve )
驱动轴承的位移y与柱塞位移占空比之间的关系为:The relationship between the displacement y of the drive bearing and the plunger displacement duty cycle is:
D1=d开1/2dmax={1-sin[2atan(|XP/YP|)]}/4D 1 =d on 1 /2d max ={1-sin[2atan(|X P /Y P |)]}/4
D2=d开2/2dmax={1-sin[2atan(|XT/YT|)]}/4D 2 =d on 2 /2d max ={1-sin[2atan(|X T /Y T |)]}/4
其中:D1为柱塞在吸油行程时高速开关高压供油阀打开吸油时的位移在整个柱塞吸、排油行程中的占空比,D2为柱塞在排油行程时高速开关排油-补油阀打开排油时的位移在整个柱塞吸、排油行程中的空比,d开1为柱塞吸油行程时高速开关高压供油阀开启时间段内的柱塞位移,d开2为柱塞排油行程时高速开关排油-补油阀开启时间段的柱塞位移,dmax为柱塞吸排油单程行程,T为需要输出的平均扭矩,Dm为液压马达的排量,P为高压油口的压力,η机为液压马达的机械效率,η阀为配油阀组的效率,YP为高速开关高压供油先导阀驱动轴承的内壁中心与柱塞缸筒中心轴线之间的固定偏置位移,XP为高速开关高压供油先导阀的位移幅值即高速开关高压供油先导阀驱动轴承的位移,YT为高速开关排油-补油先导阀驱动轴承的内壁中心与柱塞缸筒中心轴线之间的固定偏置位移,XT为高速开关排油-补油先导阀的位移幅值即高速开关排油-补油先导阀驱动轴承的位移;Among them: D 1 is the duty ratio of the displacement of the plunger in the whole plunger suction and discharge stroke when the high-speed switch high-pressure oil supply valve is opened for oil suction during the oil suction stroke, D 2 is the high-speed switch discharge of the plunger in the oil discharge stroke The displacement of the oil-supplement valve when it is opened to discharge oil is the empty ratio in the entire plunger suction and oil discharge stroke, dopen1 is the displacement of the plunger during the opening period of the high-speed switch high-pressure fuel supply valve during the plunger suction stroke, d Open 2 is the displacement of the plunger during the opening period of the high-speed switch oil discharge-replenishment valve during the oil discharge stroke of the plunger, d max is the one-way stroke of oil suction and discharge of the plunger, T is the average torque to be output, and D m is the displacement of the hydraulic motor P is the pressure of the high-pressure oil port, η machine is the mechanical efficiency of the hydraulic motor, η valve is the efficiency of the oil distribution valve group, Y P is the inner wall center of the high-speed switch high-pressure oil supply pilot valve drive bearing and the center of the plunger cylinder The fixed offset displacement between the axes, X P is the displacement amplitude of the high-speed switch high-pressure oil supply pilot valve, that is, the displacement of the high-speed switch high-pressure oil supply pilot valve drive bearing, Y T is the high-speed switch oil discharge-fill oil pilot valve drive bearing The fixed offset displacement between the center of the inner wall and the central axis of the plunger cylinder, X T is the displacement amplitude of the high-speed switch drain-fill pilot valve, that is, the displacement of the drive bearing of the high-speed switch drain-fill pilot valve;
(4)处于马达工况时,对于高速开关高压供油先导阀驱动轴承,液压马达正转时,XP<0,液压马达反转时,则XP>0;对于高速开关排油-补油先导阀驱动轴承,液压马达正转时,XT=+Max,液压马达反转时,则XT=-Max;处于泵工况时,对于高速开关高压供油先导阀驱动轴承,液压泵正反转时,XP=0;对于高速开关排油-补油先导阀驱动轴承,液压泵正转时,XT>0,液压泵反转时,则XT<0;YP>0,YT<0为固定偏置。(4) In the motor working condition, for the high-speed switch high-pressure oil supply pilot valve drive bearing, when the hydraulic motor rotates forward, X P <0, and when the hydraulic motor reverses, then X P >0; For oil pilot valve drive bearings, when the hydraulic motor is rotating forward, X T =+Max, when the hydraulic motor is reverse, then X T =-Max; when it is in the pump working condition, for the high-speed switch high-pressure oil supply pilot valve drive bearings, the hydraulic pump When forward and reverse, X P = 0; for the high-speed switch oil discharge-supplement pilot valve drive bearing, when the hydraulic pump is forward, X T > 0, when the hydraulic pump is reverse, then X T <0; Y P >0 , Y T <0 is a fixed bias.
通过上述结构与控制方法,马达工况正转时,XP<0,XT=+Max,每个柱塞每转一圈,都经历了6个状态(4个主状态和2个过渡状态):Through the above structure and control method, when the motor is running forward, X P <0, X T =+Max, each plunger has gone through 6 states (4 main states and 2 transition states ):
(1)状态A:高压驱动状态:高速开关高压供油先导阀位移小于负的高速开关高压供油先导阀驱动轴承与柱塞缸筒中心轴线之间的固定偏置(-YP),高速开关排油-补油先导阀位移大于高速开关排油-补油先导阀驱动轴承与柱塞缸筒中心轴线之间的固定偏置(YT),且柱塞前进;在高速开关高压供油先导阀的作用下,柱塞腔与高速开关高压供油阀弹簧腔沟通时,高速开关高压供油阀在高压油口的压力作用下打开,因而柱塞腔的压力接近但略低于高压油口的压力,柱塞腔同时与高速开关排油-补油阀弹簧腔沟通,高速开关排油-补油阀在柱塞腔的压力作用下保持关闭;(1) State A: High-pressure driving state: the displacement of the high-speed switching high-pressure oil supply pilot valve is smaller than the negative high- speed switching high-pressure oil supply pilot valve. The displacement of the switch oil discharge-replenishment pilot valve is greater than the fixed offset (Y T ) between the drive bearing of the high-speed switch oil discharge-replenishment pilot valve and the center axis of the plunger cylinder, and the plunger advances; Under the action of the pilot valve, when the plunger cavity communicates with the spring cavity of the high-speed switch high-pressure oil supply valve, the high-speed switch high-pressure oil supply valve opens under the pressure of the high-pressure oil port, so the pressure in the plunger cavity is close to but slightly lower than that of the high-pressure oil supply valve. At the same time, the plunger chamber communicates with the spring chamber of the high-speed switch oil discharge-replenishment valve, and the high-speed switch oil discharge-replenishment valve is kept closed under the pressure of the plunger chamber;
(2)状态B,C:空行程状态:其中B为过渡状态,C为补油状态;高速开关高压供油先导阀位移大于负的高速开关高压供油先导阀驱动轴承与柱塞缸筒中心轴线之间的固定偏置,高速开关排油-补油先导阀位移大于高速开关排油-补油先导阀驱动轴承与柱塞缸筒中心轴线之间的固定偏置,且柱塞前进;在高速开关高压供油先导阀的作用下,高压油口与高速开关高压供油阀弹簧腔沟通,高速开关高压供油阀在高压油口的压力作用下快速关闭,柱塞继续前进导致柱塞腔体积增加,压力快速降到低于回油口的背压,柱塞腔同时与高速开关排油-补油阀弹簧腔沟通,排油-补油阀在柱塞腔的压力降低到回油口背压以下后打开,其中高速开关排油-补油阀打开的过程为过渡状态B;高速开关排油-补油阀打开后柱塞从回油口补油直到到达吸排油分界面的过程为补油状态C;(2) State B, C: idle stroke state: where B is the transition state, and C is the fuel supply state; the displacement of the high-speed switch high-pressure oil supply pilot valve is greater than the negative high-speed switch high-pressure oil supply pilot valve drive bearing and the center of the plunger cylinder The fixed offset between the axes, the displacement of the high-speed switch oil drain-fill pilot valve is greater than the fixed offset between the driving bearing of the high-speed switch oil drain-fill pilot valve and the central axis of the plunger cylinder, and the plunger advances; Under the action of the high-speed switch high-pressure oil supply pilot valve, the high-pressure oil port communicates with the spring cavity of the high-speed switch high-pressure oil supply valve, and the high-speed switch high-pressure oil supply valve closes quickly under the pressure of the high-pressure oil port, and the plunger continues to move forward to cause the plunger cavity As the volume increases, the pressure quickly drops below the back pressure of the oil return port, and the plunger chamber communicates with the spring chamber of the high-speed switch oil discharge-replenishment valve at the same time, and the pressure in the plunger chamber of the oil discharge-replenishment valve drops to the oil return port Open after the back pressure is below, and the process of opening the high-speed switch oil discharge-replenishment valve is transition state B; after the high-speed switch oil discharge-replenishment valve is opened, the process of the plunger replenishing oil from the oil return port until reaching the oil suction and discharge interface is the replenishment Oil state C;
(3)状态D:正常回油状态:高速开关高压供油先导阀位移大于负的高速开关高压供油先导阀驱动轴承与柱塞缸筒中心轴线之间的固定偏置,高速开关排油-补油先导阀位移大于高速开关排油-补油先导阀驱动轴承与柱塞缸筒中心轴线之间的固定偏置,且柱塞后退;在高速开关高压供油先导阀的作用下,高速开关高压供油阀弹簧腔与高压油口连通,高压供油阀保持关闭;带背压的回油口与高速开关排油-补油阀弹簧腔沟通,由于柱塞排油时,柱塞腔压力接近并略高于带背压的回油口压力,故高速开关排油-补油阀在柱塞腔的压力作用下保持打开状态进行正常回油;(3) State D: Normal oil return state: the displacement of the high-speed switch high-pressure oil supply pilot valve is greater than the negative fixed offset between the drive bearing of the high-speed switch high-pressure oil supply pilot valve and the central axis of the plunger cylinder, and the high-speed switch discharges oil- The displacement of the oil supplement pilot valve is greater than the fixed offset between the high-speed switch oil discharge-oil supplement pilot valve drive bearing and the central axis of the plunger cylinder, and the plunger retreats; under the action of the high-speed switch high-pressure oil supply pilot valve, the high-speed switch The spring chamber of the high-pressure oil supply valve is connected with the high-pressure oil port, and the high-pressure oil supply valve remains closed; the oil return port with back pressure communicates with the spring chamber of the high-speed switch oil discharge-supplement valve, because when the plunger discharges oil, the pressure in the plunger chamber It is close to and slightly higher than the pressure of the oil return port with back pressure, so the high-speed switch drain-fill valve remains open under the pressure of the plunger cavity for normal oil return;
(4)状态E,F:泵输出状态:其中E为过渡状态,F为泵输出状态;高速开关高压供油先导阀位移大于负的高速开关高压供油先导阀驱动轴承与柱塞缸筒中心轴线之间的固定偏置,高速开关排油-补油先导阀位移小于高速开关排油-补油先导阀驱动轴承与柱塞缸筒中心轴线之间的固定偏置,且柱塞后退;在高速开关排油-补油先导阀的作用下,柱塞腔与高速开关排油-补油阀弹簧腔沟通,高速开关排油-补油阀在柱塞腔的压力作用下关闭,柱塞继续后退导致柱塞腔体积减小,压力快速上升到超过高压油口的压力,高压油口同时与高压供油阀弹簧腔沟通,高速开关高压供油阀在柱塞腔的压力上升到高压油口压力以上后打开;其中状态E为高速开关高压供油阀开启过程这一过渡状态,状态F为柱塞通过向高压油口排油直到柱塞转到排吸油分界面。(4) State E, F: pump output state: where E is the transition state, F is the pump output state; the displacement of the high-speed switch high-pressure oil supply pilot valve is greater than the negative high-speed switch high-pressure oil supply pilot valve drive bearing and the center of the plunger cylinder The fixed offset between the axes, the displacement of the high-speed switch oil drain-fill pilot valve is smaller than the fixed offset between the driving bearing of the high-speed switch oil drain-fill pilot valve and the central axis of the plunger cylinder, and the plunger retreats; Under the action of the high-speed switch drain-fill pilot valve, the plunger cavity communicates with the spring cavity of the high-speed switch drain-fill valve, and the high-speed switch drain-fill valve closes under the pressure of the plunger cavity, and the plunger continues to The retreat causes the volume of the plunger chamber to decrease, and the pressure rises rapidly to exceed the pressure of the high-pressure oil port. The high-pressure oil port communicates with the spring chamber of the high-pressure oil supply valve at the same time, and the pressure in the plunger chamber of the high-speed switch high-pressure oil supply valve rises to the pressure of the high-pressure oil port. Open after the pressure is above; the state E is the transition state of the high-speed switch high-pressure oil supply valve opening process, and the state F is the plunger discharges oil to the high-pressure oil port until the plunger turns to the oil-discharging interface.
马达工况反转以及泵工况正、反转也要经历同样的六个状态。The reverse rotation of the motor working condition and the forward and reverse rotation of the pump working condition also go through the same six states.
与现有技术相比,本实用新型的有益效果是:Compared with the prior art, the beneficial effects of the utility model are:
(1)变扭矩控制:本实用新型通过对高速开关高压供油阀开启时间段内的柱塞位移在整个柱塞吸油行程中占空比的实时调节,输出与占空比成正比的平均扭矩,实现了开关变扭矩控制,开关变扭矩控制既没有改变液压马达的排量,也没有改变供油压力,但它最终直接改变了液压马达的输出扭矩;(1) Variable torque control: the utility model outputs an average torque proportional to the duty ratio through the real-time adjustment of the duty cycle of the plunger displacement during the opening period of the high-speed switch high-pressure oil supply valve in the entire plunger oil suction stroke , realize the switch variable torque control, the switch variable torque control neither changes the displacement of the hydraulic motor, nor changes the oil supply pressure, but it directly changes the output torque of the hydraulic motor in the end;
(2)节能:当负载扭矩较小的时候,部分位于吸油区的柱塞腔不再从高压油口吸油,而是通过高速开关排油-补油阀从回油口吸油,不需要把压力油浪费在额外的节流控制阀口上,因而节约了大量的能耗;(2) Energy saving: when the load torque is small, some of the plunger chambers located in the oil suction area no longer suck oil from the high-pressure oil port, but use the high-speed switch oil discharge-suction valve to suck oil from the oil return port, and there is no need to reduce the pressure Oil is wasted on the extra throttling control valve port, thus saving a lot of energy consumption;
(3)泵工况:当同时减小柱塞在吸油行程时高速开关高压供油阀打开吸油时的位移在整个柱塞吸、排油行程中的占空比D1和柱塞在排油行程时高速开关排油-补油阀打开排油时的位移在整个柱塞吸、排油行程中的占空比和D2时,液压马达就平稳地进入了泵的工况,即输出与旋转方向相反的转矩,同时向高压油口排出高压油;(3) Pump working condition: when the plunger is in the oil suction stroke , the displacement of the high-speed switch high-pressure oil supply valve is opened when the oil is sucked. During the stroke, when the displacement of the high-speed switch oil discharge-supplement valve is opened and the oil discharge is at the duty ratio of the entire plunger suction and oil discharge stroke and D2 , the hydraulic motor enters the working condition of the pump smoothly, that is, the output and Torque in the opposite direction of rotation, while discharging high-pressure oil to the high-pressure oil port;
(4)响应速度提高一个数量级:传统液压马达中各柱塞产生的液压力,在驱动液压马达旋转的同时,其作用在斜盘上的力还会产生一个与斜盘倾斜角度控制方向一致的扭矩,且该扭矩随着液压马达转角的改变而变化,尽量有多个柱塞但仍然无法完全在内部相互抵消,这部分波动的扭矩最终都加在了控制斜盘倾斜角度的变量机构上,变量机构为了克服该波动的扭矩,需要有相当大的面积来驱动,严重限制了液压马达的响应速度;而本实用新型把变量驱动机构从斜盘的巨大不均衡力矩中解放出来,只需要克服各先导阀作用在变扭矩驱动轴承上的不均衡力,不均衡力缩小了一个数量级,从而将液压马达的变量响应速度提高了一个数量级;(4) The response speed is increased by an order of magnitude: the hydraulic force generated by each plunger in the traditional hydraulic motor drives the hydraulic motor to rotate, and the force acting on the swash plate also produces a force that is consistent with the control direction of the swash plate inclination angle. Torque, and the torque changes with the change of the hydraulic motor rotation angle. There are as many plungers as possible, but they still cannot completely cancel each other internally. This part of the fluctuating torque is finally added to the variable mechanism that controls the tilt angle of the swash plate. In order to overcome the fluctuating torque, the variable mechanism needs a relatively large area to drive, which seriously limits the response speed of the hydraulic motor; and the utility model liberates the variable driving mechanism from the huge unbalanced moment of the swash plate, and only needs to overcome The unbalanced force of each pilot valve on the variable torque drive bearing is reduced by an order of magnitude, thereby increasing the variable response speed of the hydraulic motor by an order of magnitude;
(5)避免了过零问题:传统液压马达切换为泵工况的临界点是排量为零的点,因此为了切换为泵工况以回收减速、制动过程的能量,液压马达的排量调节机构必须过零点,不仅变量机构的行程大,响应速度慢,而且还很容易导致在零点附近的不稳定;而本实用新型只需同时减小占空比D1和D2,液压马达就平稳地进入了泵的工况,不需要经过排量零点,因而也不存在零点附近的不稳定问题。(5) The zero-crossing problem is avoided: the critical point for the traditional hydraulic motor to switch to the pump working condition is the point where the displacement is zero. The adjustment mechanism must cross the zero point, not only the stroke of the variable mechanism is large, the response speed is slow, but also it is easy to cause instability near the zero point; and the utility model only needs to reduce the duty cycle D 1 and D 2 at the same time, and the hydraulic motor will It enters the working condition of the pump smoothly without going through the zero point of displacement, so there is no instability problem near the zero point.
(6)正反转切换只需改变先导阀驱动方向:当泵/马达需要切换旋转方向时,只需要按照变扭距操作步骤(4)中描述控制先导阀即可实现正反转。(6) Forward and reverse switching only needs to change the driving direction of the pilot valve: when the pump/motor needs to switch the rotation direction, only need to control the pilot valve according to the description in (4) of the variable torque operation step to realize forward and reverse rotation.
附图说明Description of drawings
图1是本实用新型结构示意图。Fig. 1 is the structural representation of the utility model.
图2是本实用新型中高速开关高压供油阀及其先导阀示意图。Fig. 2 is a schematic diagram of the high-speed switching high-pressure oil supply valve and its pilot valve of the utility model.
图3是本实用新型中高速开关排油-补油阀及其先导阀示意图。Fig. 3 is a schematic diagram of the high-speed switch oil discharge-replenishment valve and its pilot valve of the utility model.
图4是本实用新型中配油阀组与高、低压旋转支撑组件和后盖示意图。Fig. 4 is a schematic diagram of the oil distribution valve group, the high and low pressure rotating support assembly and the rear cover in the utility model.
图5是本实用新型中高速开关高压供油先导阀和其驱动轴承所在剖面。Fig. 5 is the section where the high-speed switch high-pressure oil supply pilot valve and its driving bearing are located in the utility model.
图6是本实用新型中高速开关排油-补油先导阀和其驱动轴承所在剖面。Fig. 6 is the cross-section where the high-speed switch oil discharge-oil replenishment pilot valve and its driving bearing are located in the utility model.
图7是本实用新型中配油组件各主阀和其变扭距驱动轴承安装示意图。Fig. 7 is a schematic diagram of the installation of each main valve of the oil distribution assembly and its variable torque driving bearing in the utility model.
图8是本实用新型中高速开关高压供油先导阀芯向先导阀体中安装的示意图。Fig. 8 is a schematic diagram of installation of the high-speed switch high-pressure oil supply pilot valve core into the pilot valve body of the utility model.
图9是本实用新型中高速开关排油-补油先导阀芯向先导阀体中安装的示意图。Fig. 9 is a schematic diagram of installation of the high-speed oil discharge-replenishment pilot valve core in the pilot valve body of the utility model.
图10是本实用新型中各先导阀体上面各个阀口台阶与液压油口的对应关系图。Fig. 10 is a corresponding relationship diagram between each valve port step and hydraulic oil port on each pilot valve body in the utility model.
图11是本实用新型中高速开关高压供油先导阀芯上面,各个阀口台阶与液压油口的对应关系图。Fig. 11 is a diagram of the corresponding relationship between each valve port step and the hydraulic oil port on the high-speed switch high-pressure oil supply pilot spool of the utility model.
图12是本实用新型中高速开关排油-补油先导阀芯上面,各个阀口台阶与液压油口的对应关系图。Fig. 12 is a diagram of the corresponding relationship between each valve port step and the hydraulic oil port on the top of the oil discharge-replenishment pilot valve core of the medium and high speed switch of the present invention.
图13是本实用新型各柱塞位置与其相关阀的动作流程控制图。Fig. 13 is a control diagram of the action flow of each plunger position and its associated valves in the present invention.
图14是本实用新型中各先导阀及其驱动轴承在状态A的位置示意图Figure 14 is a schematic diagram of the position of each pilot valve and its drive bearing in state A in the utility model
图15是本实用新型各主阀与其先导阀在状态A的位置示意图。Fig. 15 is a schematic diagram of the position of each main valve and its pilot valve in state A of the present invention.
图16是本实用新型各主阀与其先导阀在状态A的局部位置示意图。Fig. 16 is a schematic diagram of the partial positions of the main valves and their pilot valves in state A of the present invention.
图17是本实用新型各主阀与其先导阀在状态B的局部位置示意图。Fig. 17 is a schematic diagram of the local positions of the main valves and their pilot valves in state B of the present invention.
图18是本实用新型各主阀与其先导阀在状态C的局部位置示意图。Fig. 18 is a schematic diagram of the local positions of each main valve and its pilot valve in state C of the present invention.
图19是本实用新型各主阀与其先导阀在状态D的局部位置示意图。Fig. 19 is a schematic diagram of the partial positions of each main valve and its pilot valve in state D of the present invention.
图20是本实用新型各主阀与其先导阀在状态E的局部位置示意图。Fig. 20 is a schematic diagram of the local positions of each main valve and its pilot valve in state E of the present invention.
图21是本实用新型各主阀与其先导阀在状态F的局部位置示意图。Fig. 21 is a schematic diagram of the partial positions of the main valves and their pilot valves in state F of the present invention.
图中,1柱塞缸筒、2柱塞腔分油阀体、3主阀体、4先导阀体、5配油盘、6高速开关高压供油先导阀驱动轴承、7高速开关排油-补油先导阀驱动轴承、8高速开关高压供油先导阀、9高速开关排油-补油先导阀、10高速开关高压供油阀套、11高速开关高压供油阀芯、12高速开关高压供油阀弹簧、13高速开关排油-补油阀套、14高速开关排油-补油阀芯、15高速开关排油-补油阀弹簧、16中心柱塞腔、17柱塞腔、18配油盘高压油流道、19配油盘回油流道、20高速开关高压供油阀轴向油口、21高速开关高压供油阀周向油口、22高速开关高压供油阀弹簧腔、23高速开关高压供油先导阀靠近壳体侧端面、24高速开关高压供油先导阀靠近壳体侧端面与高速开关高压供油先导阀高压供油控制台阶之间的容腔、25高速开关高压供油先导阀高压供油控制台阶、26高速开关高压供油先导阀高压供油控制台阶与高速开关高压供油先导阀靠近中心侧端面之间的容腔、27高速开关高压供油先导阀靠近中心侧端面、28高速开关排油-补油阀轴向油口、29高速开关排油-补油阀周向油口、30高速开关排油-补油阀弹簧腔、31高速开关排油-补油先导阀靠近壳体侧端面、32高速开关排油-补油先导阀靠近壳体侧端面与高速开关排油-补油先导阀排油-补油控制台阶之间的容腔、33高速开关排油-补油先导阀排油-补油控制台阶、34高速开关排油-补油先导阀排油-补油控制台阶与高速开关排油-补油先导阀排油-补油控制台阶靠近中心侧端面之间的容腔、35高速开关排油-补油先导阀靠近中心侧端面、36密封圈、37高速开关高压供油先导阀靠近壳体侧端面与高压供油控制台阶之间的容腔与柱塞腔的通道、38高速开关排油-补油先导阀靠近壳体侧端面与排油-补油控制台阶之间的容腔与柱塞腔连接通道、39高速开关高压供油先导阀高压供油控制台阶靠近中心侧端面与高速开关高压供油先导阀靠近中心侧端面之间的容腔与配油阀组高压油流道连接通道、40高速开关排油-补油先导阀排油-补油控制台阶靠近中心侧端面与高速开关排油-补油先导阀靠近中心侧端面之间的容腔与配油阀组高压油流道连接通道、41高速开关高压供油先导阀高压供油控制台阶与高速开关高压供油阀弹簧腔连接通道、42高速开关排油-补油先导阀排油-补油控制台阶与高速开关排油-补油阀弹簧腔连接通道、43高速开关高压供油先导阀高压供油控制台阶靠近中心侧端面与高速开关高压供油先导阀靠近中心侧端面之间的容腔与高速开关高压供油阀周向油口连接通道、44高速开关排油-补油先导阀排油-补油控制台阶靠近中心侧端面与高速开关排油-补油先导阀靠近中心侧端面之间的容腔与高速开关排油-补油阀周向油口连接通道、45控制驱动外壳、46高速开关高压供油先导阀驱动轴承控制阀体、47高速开关高压供油先导阀驱动轴承控制柱塞、48高速开关高压供油先导阀驱动轴承控制弹簧、49高速开关高压供油先导阀驱动轴承控制弹簧压片、50高速开关排油-补油先导阀驱动轴承控制阀体、51高速开关排油-补油先导阀驱动轴承控制柱塞、52高速开关排油-补油先导阀驱动轴承控制弹簧、53高速开关排油-补油先导阀驱动轴承控制弹簧压片、54高压旋转支撑组件、55低压旋转支撑组件、56后端盖、57高压油口、58回油口、59高速开关高压供油先导阀驱动轴承控制柱塞弹簧腔、60高速开关排油-补油先导阀驱动轴承控制柱塞弹簧腔。In the figure, 1 plunger cylinder, 2 plunger chamber oil distribution valve body, 3 main valve body, 4 pilot valve body, 5 oil distribution plate, 6 high-speed switch high-pressure oil supply pilot valve driving bearing, 7 high-speed switch oil discharge- Oil supply pilot valve driving bearing, 8 high-speed switch high-pressure oil supply pilot valve, 9 high-speed switch oil discharge-oil supply pilot valve, 10 high-speed switch high-pressure oil supply valve sleeve, 11 high-speed switch high-pressure oil supply spool, 12 high-speed switch high-pressure supply Oil valve spring, 13 high-speed switch drain-fill valve sleeve, 14 high-speed switch drain-fill valve core, 15 high-speed switch drain-fill valve spring, 16 center plunger chamber, 17 plunger chamber, 18 fitting High-pressure oil flow channel of oil pan, 19 return oil flow channel of oil distribution plate, 20 axial oil port of high-speed switch high-pressure oil supply valve, 21 circumferential oil port of high-speed switch high-pressure oil supply valve, 22 spring chamber of high-speed switch high-pressure oil supply valve, 23 The high-speed switch high-pressure oil supply pilot valve is close to the end face of the shell side, 24 The high-speed switch high-pressure oil supply pilot valve is close to the cavity between the shell side end face and the high-speed switch high-pressure oil supply pilot valve, the high-pressure oil supply console step, 25 The high-speed switch high pressure Oil supply pilot valve high-pressure oil supply console step, 26 high-speed switch high-pressure oil supply pilot valve high-pressure oil supply console step and the cavity between the high-speed switch high-pressure oil supply pilot valve near the center side end face, 27 high-speed switch high-pressure oil supply pilot valve close Center side end face, 28 high-speed switch oil discharge-replenishment valve axial port, 29 high-speed switch oil discharge-replenishment valve circumferential port, 30 high-speed switch oil discharge-replenishment valve spring chamber, 31 high-speed switch oil discharge- The oil charge pilot valve is close to the end face of the shell side, the cavity between the high-speed switch oil discharge-oil charge pilot valve near the end face of the shell side and the high-speed switch oil discharge-oil charge pilot valve oil discharge-oil charge console step, 33 high speed Switch oil discharge-oil replenishment pilot valve oil discharge-oil replenishment console stage, 34 high-speed switch oil discharge-oil replenishment pilot valve oil discharge-oil replenishment console stage and high-speed switch oil discharge-oil replenishment pilot valve oil discharge-oil replenishment console stage Between the chamber near the end face of the center side, 35 high-speed switch oil discharge-replenishment pilot valve near the center side end face, 36 sealing ring, 37 high-speed switch between the end face of the high-pressure oil supply pilot valve near the shell side and the high-pressure oil supply console step The passage between the cavity and the plunger cavity, the connection channel between the cavity and the plunger cavity between the 38 high-speed switch oil discharge-replenishment pilot valve close to the side end surface of the shell and the oil discharge-replenishment console step, the 39 high-speed switch high-pressure supply Oil pilot valve high-pressure oil supply console step near the center side end face and the high-speed switch high-pressure oil supply pilot valve near the center side end face between the cavity and the oil distribution valve group high-pressure oil flow channel connection channel, 40 high-speed switch oil discharge-oil replenishment pilot The cavity between the end surface of the oil discharge-supplement control console near the center and the end surface of the high-speed switch oil discharge-supplement pilot valve near the center is connected to the high-pressure oil flow channel of the oil distribution valve group, and the high-pressure oil supply pilot of the 41 high-speed switch High-pressure oil supply console step of valve and high-speed switch high-pressure oil supply valve spring chamber connection channel, 42 high-speed switch oil discharge-replenishment pilot valve oil discharge-replenishment console step and high-speed switch oil discharge-replenishment valve spring chamber connection channel, 43 High-speed switch, high-pressure oil supply pilot valve, high-pressure oil supply console, end face near the center side and high-speed switch, high-pressure oil supply pilot valve, end face near the center side The cavity between the high-speed switch and the high-pressure oil supply valve is connected to the circumferential oil port, and the 44 high-speed switch oil discharge-replenishment pilot valve oil discharge-replenishment console step is close to the center side end face and the high-speed switch oil discharge-replenishment pilot valve The cavity between the end faces near the center is connected to the circumferential oil port of the high-speed switch oil drain-fill valve, 45 control drive casing, 46 high-speed switch high-pressure oil supply pilot valve drive bearing control valve body, 47 high-speed switch high-pressure oil supply Pilot valve drive bearing control plunger, 48 high-speed switch high-pressure oil supply pilot valve drive bearing control spring, 49 high-speed switch high-pressure oil supply pilot valve drive bearing control spring pressure plate, 50 high-speed switch oil discharge-oil supply pilot valve drive bearing control valve Body, 51 high-speed switch oil discharge-oil replenishment pilot valve drive bearing control plunger, 52 high-speed switch oil discharge-oil replenishment pilot valve drive bearing control spring, 53 high-speed switch oil discharge-oil replenishment pilot valve drive bearing control spring pressure piece, 54 high-pressure rotary support assembly, 55 low-pressure rotary support assembly, 56 rear end cover, 57 high-pressure oil port, 58 oil return port, 59 high-speed switch high-pressure oil supply pilot valve drive bearing control plunger spring chamber, 60 high-speed switch oil discharge-supplement The oil pilot valve drive bearing controls the plunger spring chamber.
具体实施方式Detailed ways
结合附图,下面通过具体实施例对本实用新型进行详细说明。In conjunction with the accompanying drawings, the utility model will be described in detail below through specific embodiments.
如附图所示,具体实施例中提供的吸排油独立调节的开关马达变扭矩配油机构,包括扭矩输出机构、定量斜盘、柱塞缸筒1、柱塞和柱塞腔17,还包括配油阀组、配油盘组和开关变扭矩驱动机构;As shown in the drawings, the switch motor variable torque oil distribution mechanism provided in the specific embodiment with independent adjustment of oil suction and discharge includes a torque output mechanism, a quantitative swash plate, a
所述的配油阀组由与柱塞个数相同的高速开关高压供油阀、高速开关排油-补油阀,高速开关高压供油先导阀8,高速开关排油-补油先导阀9和公共的配油主阀体3构成,每个柱塞及其相应的柱塞腔17对应一个高速开关高压供油阀及与之对应的高速开关高压供油先导阀8、一个高速开关排油-补油阀及与之对应的高速开关排油-补油先导阀9;每个高速开关高压供油阀包括一个高速开关高压供油阀套10、一个高速开关高压供油阀芯11、一个高速开关高压供油阀弹簧12、一个高速开关高压供油阀轴向油口20和一个高速开关高压供油阀周向油口21、一个高速开关高压供油阀弹簧腔22,每个高速开关排油-补油阀包括一个高速开关排油-补油阀套13、一个高速开关排油-补油阀芯14、一个高速开关排油-补油阀弹簧15、、一个高速开关排油-补油阀轴向油口28和一个高速开关排油-补油阀周向油口29一个高速开关排油-补油阀弹簧腔30;和每个高速开关排油-补油阀均包括各自的阀芯、弹簧、弹簧腔、轴向油口、周向油口;每个高速开关高压供油先导阀8均有一个高速开关高压供油先导阀高压供油控制台阶25,每个高速开关排油-补油先导阀9均有一个高速开关排油-补油先导阀排油-补油控制台阶33;在每个高速开关高压供油先导阀靠近壳体侧的端面23与其高速开关高压供油先导阀高压供油控制台阶25之间有一个高速开关高压供油先导阀靠近壳体侧端面与高速开关高压供油先导阀高压供油控制台阶之间的容腔24,高速开关高压供油先导阀高压供油控制台阶25与高速开关高压供油先导阀靠近中心侧端面27之间各有一个高速开关高压供油先导阀高压供油控制台阶与高速开关高压供油先导阀靠近中心侧端面之间的容腔26,在每个高速开关排油-补油先导阀靠近壳体侧的端面31与其高速开关排油-补油先导阀排油-补油控制台阶33之间有一个高速开关排油-补油先导阀靠近壳体侧端面与高速开关排油-补油先导阀排油-补油控制台阶之间的容腔32,高速开关排油-补油先导阀排油-补油控制台阶33与高速开关排油-补油先导阀靠近中心侧端面35之间各有一个高速开关排油-补油先导阀排油-补油控制台阶与高速开关排油-补油先导阀靠近中心侧端面之间的容腔34;每个柱塞对应的高速开关高压供油阀与高速开关排油-补油阀都并排设置,其轴向油口均与其对应的柱塞腔17连通;每个高速开关高压供油阀的周向油口21,均穿过高速开关高压供油先导阀的高压供油控制台阶与其高速开关高压供油先导阀靠近中心侧端面之间的容腔26,与配油盘组的高压油流道18连通;每个高速开关排油-补油阀的周向油口29,均穿过高速开关排油-补油先导阀的排油-补油控制台阶与其高速开关排油-补油先导阀靠近中心侧端面之间的容腔34,与配油盘的回油流道19连通;每个高速开关高压供油阀的弹簧腔22均与相应的先导阀上的高速开关高压供油先导阀高压供油控制台阶25连通,每个高速开关排油-补油阀的弹簧腔30均与相应的先导阀上的高速开关排油-补油先导阀排油-补油控制台阶33连通;每个高速开关高压供油先导阀8和高速开关排油-补油先导阀9的两个端面(靠近壳体侧端面与靠近中心侧端面)均与泄漏油口连通,每个高速开关高压供油先导阀高压供油控制台阶与高速开关高压供油先导阀靠近中心侧的端面之间的容腔26均与配油盘组的高压油流道18连通;每个高速开关排油-补油先导阀排油-补油控制台阶与高速开关排油-补油先导阀靠近中心侧端面之间的容腔34均与配油盘的回油流道连通;每个高速开关高压供油先导阀靠近壳体侧端面与其高速开关高压供油先导阀高压共供油控制台阶之间的容腔24均与相应的柱塞腔17相连,每个高速开关排油-补油先导阀靠近壳体侧端面与其高速开关排油-补油先导阀排油-补油控制台阶之间的容腔32均与相应的柱塞腔17相连;所有高速开关高压供油先导阀8位于同一截面上,所有高速开关排油-补油先导阀9位于同一截面上;The oil distribution valve group is composed of a high-speed switching high-pressure oil supply valve, a high-speed switching oil drain-fill valve, a high-speed switch high-pressure oil
所述的配油盘组与所述的配油先导阀体4位于柱塞另一侧的端面接触,无相对运动,配油盘组内部有配油盘高压油流道18和配油盘回油流道19;配油盘组中心的配油盘高压油流道18与所述配油阀组上所有高速开关高压供油先导阀在高速开关高压供油先导阀高压供油控制台阶与高速开关高压供油先导阀靠近中心侧端面之间的容腔26连通,配油盘组上的配油盘高压油流道18与壳体后端盖56上的高压油口57连通;配油盘组中心配油盘高压油流道18外侧的环形配油盘回油流道19与所述配油阀组上所有高速开关排油-补油先导阀在高速开关排油-补油先导阀排油-补油控制台阶与高速开关排油-补油先导阀靠近中心侧端面之间的容腔34连通,配油盘组上的环形配油盘回油流道19与壳体后端盖56上的回油油口58连通;泄漏油流道与泵本体上的泄漏油流道共用,与壳体上的泄漏油口连通;所述的配油盘组中心配油盘高压油流道18与其外侧的环形配油盘回油流道19之间,中心高压油流道外侧的环形配油盘回油流道19与靠近壳体侧的泄漏油流道之间分别采用高压旋转支撑组件54和低压旋转支撑组件55提供旋转支撑,配油盘组与壳体后端盖56之间相对转动。The oil distribution plate group is in contact with the end face of the oil distribution
吸排油独立调节的开关马达变扭矩配油机构,其开关变扭矩驱动机构分为高压供油驱动机构和排油-补油驱动机构,其中高压供油驱动机构由一个高速开关高压供油先导阀驱动轴承6及两个高速开关高压供油先导阀驱动轴承控制阀体控制柱塞46、两个高速开关高压供油先导阀驱动轴承控制柱塞47阀体、两个高速开关高压供油先导阀驱动轴承控制弹簧48、两个高速开关高压供油先导阀驱动轴承控制弹簧压片49和与弹簧对应的两个高速开关高压供油先导阀驱动轴承控制柱塞弹簧腔59组成,排油-补油驱动机构由一个高速开关排油-补油先导阀驱动轴承7及两个高速开关排油-补油先导阀驱动轴承控制阀体50控制柱塞、两个高速开关排油-补油先导阀驱动轴承控制柱塞51阀体、两个高速开关排油-补油先导阀驱动轴承控制弹簧52、两个高速开关排油-补油先导阀驱动轴承控制弹簧压片53和与弹簧对应的两个高速开关排油-补油先导阀驱动轴承控制柱塞弹簧腔60组成;高速开关高压供油驱动机构的两个高速开关高压供油先导阀驱动轴承控制柱塞47与于高速开关高压供油先导阀驱动轴承6轴线垂直,与该轴承运动方向所在直线共线,与该轴承外圈相切,圆周方向均布,每个高速开关高压供油先导阀驱动轴承控制柱塞47与高速开关高压供油先导阀驱动轴承6外圈不接触的另一端面安装高速开关高压供油先导阀驱动轴承控制弹簧48,高速开关高压供油先导阀驱动轴承控制弹簧48的另一端面设置高速开关高压供油先导阀驱动轴承控制弹簧压片49,高速开关高压供油先导阀驱动轴承控制柱塞47、高速开关高压供油先导阀驱动轴承控制弹簧48、高速开关高压供油先导阀驱动轴承控制弹簧压片49均位于高速开关高压供油先导阀驱动轴承控制柱塞阀体46内,其内部的高速开关高压供油先导阀驱动轴承控制弹簧腔59与外部的控制油路连通,高速开关高压供油先导阀驱动轴承控制柱塞阀体46与高速开关高压供油先导阀驱动轴承控制柱塞47同轴,安装在控制驱动外壳45上,高速开关高压供油先导阀驱动轴承6内圈与其驱动的高速开关高压供油先导阀8上的高速开关高压供油先导阀靠近壳体侧端面23接触并提供旋转支撑;高速开关排油-补油驱动机构的两个高速开关排油-补油先导阀驱动轴承控制柱塞51与于高速开关排油-补油高压供油先导阀驱动轴承7轴线垂直,与该轴承运动方向所在直线共线,与该轴承外圈相切,圆周方向均布,每个高速开关排油-补油先导阀驱动轴承控制柱塞51与高速开关排油-补油先导阀驱动轴承7外圈不接触的另一端面安装高速开关排油-补油先导阀驱动轴承控制弹簧52,高速开关排油-补油先导阀驱动轴承控制弹簧52的另一端面设置高速开关排油-补油先导阀驱动轴承控制弹簧压片53,高速开关排油-补油先导阀驱动轴承控制柱塞51、高速开关排油-补油先导阀驱动轴承控制弹簧52、高速开关排油-补油先导阀驱动轴承控制弹簧压片53均位于高速开关排油-补油先导阀驱动轴承控制柱塞阀体50内,其内部的高速开关排油-补油先导阀驱动轴承控制弹簧腔60与外部的控制油路连通,高速开关排油-补油先导阀驱动轴承控制柱塞阀体50与高速开关排油-补油先导阀驱动轴承控制柱塞51同轴,安装在控制驱动外壳45上,高速开关排油-补油先导阀驱动轴承7内圈与其驱动的高速开关排油-补油先导阀9上的高速开关排油-补油先导阀靠近壳体侧端面31接触并提供旋转支撑;高速开关高压供油先导阀驱动轴承6只控制高速开关高压供油先导阀8,高速开关高压供油先导阀8只控制高速开关高压供油阀,高速开关排油-补油先导阀驱动轴承7只控制高速开关排油-补油先导阀9,高速开关排油-补油先导阀9只控制高速开关排油-补油阀,如此实现了配油机构的吸、排油单独控制独立调节。The switch motor variable torque oil distribution mechanism with independent adjustment of oil suction and discharge, the switch variable torque drive mechanism is divided into high-pressure oil supply drive mechanism and oil discharge-oil replenishment drive mechanism, in which the high-pressure oil supply drive mechanism is composed of a high-speed switch high-pressure oil supply pilot valve Drive bearing 6 and two high-speed switch high-pressure oil supply pilot valve drive bearing control valve body control plunger 46, two high-speed switch high-pressure oil supply pilot valve drive bearing control plunger 47 valve body, two high-speed switch high-pressure oil supply pilot valve Drive bearing control spring 48, two high-speed switch high-pressure oil supply pilot valve drive bearing control spring pressing plate 49 and two high-speed switch high-pressure oil supply pilot valve drive bearing control plunger spring chamber 59 corresponding to the spring, oil discharge-fill The oil driving mechanism consists of a high-speed switch oil discharge-oil replenishment pilot valve drive bearing 7 and two high-speed switch oil discharge-oil replenishment pilot valve drive bearings to control the valve body 50 to control the plunger, two high-speed oil discharge-oil replenishment pilot valves Drive bearing control plunger 51 valve body, two high-speed switch oil discharge-oil replenishment pilot valve drive bearing control springs 52, two high-speed switch oil discharge-oil replenishment pilot valve drive bearing control spring pressing pieces 53 and two corresponding springs A high-speed switch oil discharge-oil replenishment pilot valve drive bearing control plunger spring cavity 60 is composed of two high-speed switch high-pressure oil supply pilot valve drive bearing control plungers 47 of the high-speed switch high-pressure oil supply drive mechanism and the high-speed switch high-pressure oil supply drive mechanism Pilot valve driving bearing 6 is perpendicular to the axis, collinear with the straight line where the direction of motion of the bearing is, tangent to the outer ring of the bearing, and evenly distributed in the circumferential direction. The other end surface of the oil supply pilot valve drive bearing 6 that does not contact the outer ring is installed with a high-speed switch high-pressure oil supply pilot valve drive bearing control spring 48, and the other end surface of the high-speed switch high-pressure oil supply pilot valve drive bearing control spring 48 is provided with a high-speed switch high-pressure supply Oil pilot valve drive bearing control spring pressure piece 49, high-speed switch high-pressure oil supply pilot valve drive bearing control plunger 47, high-speed switch high-pressure oil supply pilot valve drive bearing control spring 48, high-speed switch high-pressure oil supply pilot valve drive bearing control spring pressure The pieces 49 are all located in the high-speed switch high-pressure oil supply pilot valve drive bearing control plunger valve body 46, and the high-speed switch high-pressure oil supply pilot valve drive bearing control spring chamber 59 is connected with the external control oil circuit, and the high-speed switch high-pressure oil supply The pilot valve drive bearing control plunger valve body 46 is coaxial with the high-speed switch high-pressure oil supply pilot valve drive bearing control plunger 47, and is installed on the control drive housing 45. The high-speed switch high-pressure oil supply pilot valve drive bearing 6 inner ring and its drive The high-speed switch high-pressure oil
配油盘组由配油盘5、高压旋转支撑组件54、低压旋转支撑组件55和后端盖56组成,与吸、排油腰形孔以吸排油分界面为中心对称分布的传统配油盘不同,配油盘5内部有配油盘高压油流道18和配油盘回油流道19,中心圆柱状流道作为配油盘高压油流道18,配油盘高压油流道18外侧的环形流道作为配油盘回油流道19,配油盘回油流道19外壁外侧为泄露油腔;配油盘5与先导阀体4配合端面上中心圆型区域一侧与先导阀体上的高压油流道连通,另一端与配油盘上高压油流道18直接连通,圆形区域外侧的环形区域一侧与先导阀体上的回油流道连通,另一端通过4个相同的,圆周方向均布的腰形孔与配油盘上的环形回油流道19连通;高压旋转支撑组件54提供配油盘高压油流道18与配油盘回油流道19之间的密封,低压旋转支撑组件55提供配油盘回油流道19与泄漏油流道之间的密封,高压旋转支撑组件54和低压旋转支撑55组件共同提供配油盘5组件与后端盖56壳体之间的旋转支撑。The oil distribution plate group is composed of the
高速开关高压供油先导阀8轴线在高速开关阀所在平面上的投影与高速开关排油-补油先导阀9轴线在高速开关阀所在平面上的投影以吸排油分界线为轴线对称。The projection of the
高速开关高压供油先导阀驱动轴承6的内壁中心轴线与所述柱塞缸筒1的中心轴线平行,并沿着与吸排油分界线有一较小夹角的方向有一个固定偏置,高速开关高压供油先导阀驱动轴承6能且只能在该方向的垂直方向左右移动;高速开关排油-补油先导阀驱动轴承7的内壁中心轴线与所述柱塞缸筒1的中心轴线平行,并沿着与吸排油分界线有一较小夹角的方向有一个固定偏置,该方向与高速开关高压供油先导阀驱动轴承7固定偏置方向在高速开关阀所在平面的投影关于吸排油分界面对称,高速开关排油-补油先导阀驱动轴承7能且只能在该方向的垂直方向左右移动。The central axis of the inner wall of the high-speed switching high-pressure oil supply pilot
所述高速开关高压供油先导阀靠近中心侧的端面27,其直径比高速开关高压供油先导阀高压供油控制台阶25的直径略小,该面积差给高速开关高压供油先导阀8提供了一个径向的压力,使得所有的高速开关高压供油先导阀8都能够压在所述的变扭矩高速开关高压供油先导阀驱动轴承6上。;所述高速开关排油-补油先导阀靠近中心侧的端面35,其直径比高速开关排油-补油先导阀排油-补油控制台阶33的直径小,该面积差给高速开关排油-补油先导阀9提供了一个径向的压力,使得所有的高速开关排油-补油先导阀9都能够压在所述的变扭矩高速开关排油-补油先导阀驱动轴承7上。The end face 27 of the high-speed switch high-pressure oil supply pilot valve near the center has a diameter slightly smaller than the diameter of the high-speed switch high-pressure oil supply pilot valve high-pressure oil
所述的配油阀体在轴向被分成三片:柱塞腔分油阀体2、主阀体3、先导阀体4;柱塞腔分油阀体2、主阀体3、先导阀体4通过销钉刚性连接到柱塞缸筒1上,配油阀体与配油盘组通过螺钉连接在一起;柱塞腔分油阀体2与主阀体3、主阀体3与先导阀体4、先导阀体4与配油盘组、柱塞腔分油阀体2与柱塞缸筒1之间所有油口的外缘,都设有密封圈。The oil distribution valve body is divided into three pieces in the axial direction: plunger chamber oil
所述的高速开关高压供油先导阀的高压供油控制台阶25与高速开关排油-补油先导阀排油-补油控制台阶33的宽度均与先导阀体上相应的沉割槽宽度一致,使得先导阀能够快速响应柱塞位置的变化。The widths of the high-pressure oil
所述的高速开关高压供油先导阀控制驱动轴承6和高速开关排油-补油先导阀控制驱动轴承7的位移为零时,高速开关高压供油阀的弹簧腔22除了在排油-吸油过渡点被隔离外,其他位置均与配油盘组中心的配油盘高压油流道18连通,使高速开关高压供油阀保持关闭,高速开关排油-补油阀的弹簧腔30除了在吸油-排油过渡点被隔离外,其他位置均与柱塞腔17连通,使高速开关排油-补油阀保持打开,使马达能够从配油盘组的配油盘回油流道19补油。When the displacement of the high-speed switch high-pressure oil supply pilot valve
所述的高速开关高压供油先导阀控制驱动轴承6位移为零时,高速开关高压供油先导阀8的初始位移为负的高速开关高压供油先导阀驱动轴承6与柱塞缸筒1中心轴线之间的固定偏置;高速开关高压供油先导阀上的高压供油控制台阶25将高速开关高压供油阀弹簧腔22、高速开关高压供油先导阀靠近壳体侧端面与高速开关高压供油先导阀其高压供油控制台阶之间的容腔24、高速开关高压供油先导阀高压供油控制台阶靠近中心侧与高速开关高压供油先导阀靠近中心侧端面其高压供油控制台阶之间的容腔26互相隔断;所述的高速开关排油-补油先导阀控制轴承7位移为零时,高速开关排油-补油先导阀9的初始位移为两倍的高速开关排油-补油先导阀驱动轴承7与柱塞缸筒1中心轴线之间的固定偏置;高速开关排油-补油先导阀上的排油-补油控制台阶33将高速开关排油-补油阀的弹簧腔30与柱塞腔17连通,且高速开关排油-补油先导阀9阀口开度为两倍的高速开关排油-补油先导阀驱动轴承7与柱塞缸筒1中心轴线之间的固定偏置。When the high-speed switch high-pressure oil supply pilot valve controls the displacement of the driving bearing 6 to zero, the initial displacement of the high-speed switch high-pressure oil
基于前述吸排油独立调节的开关马达变扭矩配油机构,首先对初始位置以及正方向定义如下:Based on the aforementioned switch motor variable torque oil distribution mechanism with independent adjustment of oil suction and discharge, the initial position and positive direction are first defined as follows:
1.取吸排油分界线上,柱塞处于柱塞杠筒1最深处时为起始点,起始角度为0°;1. On the boundary line of suction, suction and discharge, the plunger is at the deepest point of the
2.正对输出轴,取左旋为正,右旋为负;2. Facing the output shaft, take left-handed as positive and right-handed as negative;
3.所有的先导阀驱动环轴承向右为正,向左为负;3. All pilot valve drive ring bearings are positive when they are to the right, and negative when they are to the left;
4.所有的先导阀芯向上运动为正,向下为负;4. The upward movement of all pilot spools is positive, and the downward movement is negative;
5.所有的先导阀位移中间值规定为阀芯的0位;5. The intermediate value of displacement of all pilot valves is defined as the 0 position of the spool;
6.坐标轴取正视输出轴,水平向右为X轴正方向,竖直向上为Y轴正方向;6. The coordinate axis is the output axis of the front view, the positive direction of the X-axis is horizontally to the right, and the positive direction of the Y-axis is vertically upward;
7.以柱塞缸筒1中心为原点,变量驱动轴承环向右、向上为正,向左、向下为负;7. With the center of the
该开关变扭矩方法包括以下步骤:The switch variable torque method comprises the following steps:
(1)根据对输出扭矩大小的要求,调节高速开关高压供油先导阀驱动轴承6和高速开关排油-补油先导阀驱动轴承7,用以改变各高速开关高压供油阀的开关时间占空比;(1) According to the requirements of the output torque, adjust the driving bearing 6 of the high-speed switch high-pressure oil supply pilot valve and the drive bearing 7 of the high-speed switch oil discharge-oil supply pilot valve to change the switching time of each high-speed switch high-pressure oil supply valve. empty ratio;
(2)控制高速开关高压供油阀的开启时间,使得位于吸油区的柱塞腔17,仅在高速开关高压供油阀开启时,能够从高压油口57吸油,推动相应的柱塞做功;位于吸油区的柱塞腔17在高速开关供油阀关闭时,均通过与回油口58相通的高速开关排油-补油阀,直接从回油口58吸油,补充柱塞运动产生的空腔,但不会推动柱塞做功;与此同时,位于排油区的柱塞腔,仅在高速开关高压供油阀关闭时,能够通过与回油口17相通的高速开关排油-补油阀,直接排到回油口17,不阻碍柱塞运动;位于排油区的柱塞腔17在高速开关排油-补油阀关闭时,均通过高压供油阀向高压油口57排油,工作在泵工况,实现减速与制动,并把制动能变回成压力能;确保平均输出扭矩与高速开关高压供油阀开启时间段内柱塞的位移在整个柱塞吸油行程中的占空比成正比;(2) Control the opening time of the high-speed switch high-pressure oil supply valve, so that the
(3)通过对高速开关高压供油阀开启时间段内柱塞的位移在整个柱塞吸、排油行程中占空比的实时调节,输出与占空比成正比的平均扭矩,实现变扭矩控制;占空比与平均扭矩之间的关系为:(3) Through the real-time adjustment of the duty ratio of the displacement of the plunger during the opening period of the high-speed switch high-pressure oil supply valve in the entire plunger suction and oil discharge stroke, the average torque proportional to the duty ratio is output to realize variable torque control; the relationship between the duty cycle and the average torque is:
T=[D1-(1-D2)]*(Dm×P×η机×η阀)T=[D 1 -(1-D 2 )]*(D m ×P× ηmachine × ηvalve )
驱动轴承的位移y与柱塞位移占空比之间的关系为:The relationship between the displacement y of the drive bearing and the plunger displacement duty cycle is:
D1=d开1/2dmax={1-sin[2atan(|XP/YP|)]}/4D 1 =d on 1 /2d max ={1-sin[2atan(|X P /Y P |)]}/4
D2=d开2/2dmax={1-sin[2atan(|XT/YT|)]}/4D 2 =d on 2 /2d max ={1-sin[2atan(|X T /Y T |)]}/4
其中:D1为柱塞在吸油行程时高速开关高压供油阀打开吸油时的位移在整个柱塞吸、排油行程中的占空比,D2为柱塞在排油行程时高速开关排油-补油阀打开排油时的位移在整个柱塞吸、排油行程中的空比,d开1为柱塞吸油行程时高速开关高压供油阀开启时间段内的柱塞位移,d开2为柱塞排油行程时高速开关排油-补油阀开启时间段的柱塞位移,dmax为柱塞吸排油单程行程,T为需要输出的平均扭矩,Dm为液压马达的排量,P为高压油口的压力,η机为液压马达的机械效率,η阀为配油阀组的效率,YP为高速开关高压供油先导阀驱动轴承的内壁中心与柱塞缸筒中心轴线之间的固定偏置位移,XP为高速开关高压供油先导阀的位移幅值即高速开关高压供油先导阀驱动轴承的位移,YT为高速开关排油-补油先导阀驱动轴承的内壁中心与柱塞缸筒中心轴线之间的固定偏置位移,XT为高速开关排油-补油先导阀的位移幅值即高速开关排油-补油先导阀驱动轴承的位移;Among them: D 1 is the duty ratio of the displacement of the plunger in the whole plunger suction and discharge stroke when the high-speed switch high-pressure oil supply valve is opened for oil suction during the oil suction stroke, D 2 is the high-speed switch discharge of the plunger in the oil discharge stroke The displacement of the oil-supplement valve when it is opened to discharge oil is the empty ratio in the entire plunger suction and oil discharge stroke, dopen1 is the displacement of the plunger during the opening period of the high-speed switch high-pressure fuel supply valve during the plunger suction stroke, d Open 2 is the displacement of the plunger during the opening period of the high-speed switch oil discharge-replenishment valve during the oil discharge stroke of the plunger, d max is the one-way stroke of oil suction and discharge of the plunger, T is the average torque to be output, and D m is the displacement of the hydraulic motor P is the pressure of the high-pressure oil port, η machine is the mechanical efficiency of the hydraulic motor, η valve is the efficiency of the oil distribution valve group, Y P is the inner wall center of the high-speed switch high-pressure oil supply pilot valve drive bearing and the center of the plunger cylinder The fixed offset displacement between the axes, X P is the displacement amplitude of the high-speed switch high-pressure oil supply pilot valve, that is, the displacement of the high-speed switch high-pressure oil supply pilot valve drive bearing, Y T is the high-speed switch oil discharge-fill oil pilot valve drive bearing The fixed offset displacement between the center of the inner wall and the central axis of the plunger cylinder, X T is the displacement amplitude of the high-speed switch drain-fill pilot valve, that is, the displacement of the drive bearing of the high-speed switch drain-fill pilot valve;
(4)处于马达工况时,对于高速开关高压供油先导阀驱动轴承,液压马达正转时,XP<0,液压马达反转时,则XP>0;对于高速开关排油-补油先导阀驱动轴承,液压马达正转时,XT=+Max,液压马达反转时,则XT=-Max;处于泵工况时,对于高速开关高压供油先导阀驱动轴承,液压泵正反转时,XP=0;对于高速开关排油-补油先导阀驱动轴承,液压泵正转时,XT>0,液压泵反转时,则XT<0;YP>0,YT<0为固定偏置。(4) In the motor working condition, for the high-speed switch high-pressure oil supply pilot valve drive bearing, when the hydraulic motor rotates forward, X P <0, and when the hydraulic motor reverses, then X P >0; For oil pilot valve drive bearings, when the hydraulic motor is rotating forward, X T =+Max, when the hydraulic motor is reverse, then X T =-Max; when it is in the pump working condition, for the high-speed switch high-pressure oil supply pilot valve drive bearings, the hydraulic pump When forward and reverse, X P = 0; for the high-speed switch oil discharge-supplement pilot valve drive bearing, when the hydraulic pump is forward, X T > 0, when the hydraulic pump is reverse, then X T <0; Y P >0 , Y T <0 is a fixed bias.
作为本实用新型的具体应用的一个实例,此处具体讨论了一种采用了本实用新型提供的吸、排油阀独立调节的机液先导开关变扭矩配油组件的旋转缸筒柱塞液压马达,详细描述如下:As an example of the specific application of the utility model, a rotary cylinder plunger hydraulic motor adopting the hydraulic pilot switch variable torque oil distribution assembly provided by the utility model with independent adjustment of the suction and discharge valves is discussed here , the detailed description is as follows:
拆除柱塞式定量液压马达的后盖和配油盘,将柱塞缸筒的端面加工成平面,将本实用新型的配油组件安装到液压马达原来的后盖和配油盘位置,柱塞缸筒与配油组件之间通过销钉连接。一个普通的旋转缸筒柱塞式定量液压马达就被改装成了一个具有吸、排油阀独立调节的机液先导开关变扭矩功能的液压马达了。Remove the back cover and oil distribution plate of the plunger type quantitative hydraulic motor, process the end face of the plunger cylinder into a plane, install the oil distribution assembly of the present utility model to the original position of the back cover and oil distribution plate of the hydraulic motor, and the plunger The cylinder barrel and the oil distribution assembly are connected by pins. An ordinary rotary cylinder plunger type quantitative hydraulic motor has been refitted into a hydraulic motor with a torque-variable function of a machine-hydraulic pilot switch for independent regulation of oil suction and discharge valves.
根据前面所述的结构与控制方法,该液压马达正转时的工作过程如附图13~21所示。每个柱塞每转一圈,都经历了6个状态(4个主状态和2个过渡状态):According to the aforementioned structure and control method, the working process of the hydraulic motor when it is rotating forward is shown in Figures 13-21. Each plunger goes through 6 states (4 main states and 2 transition states) per revolution:
(1)状态A:高压驱动状态:正转时,XP<0,XT>0,高速开关高压供油先导阀8位移小于负的高速开关高压供油先导阀驱动轴承6与柱塞缸筒1中心轴线之间的固定偏置,高速开关排油-补油先导阀9位移大于高速开关排油-补油先导阀驱动轴承7与柱塞缸筒1中心轴线之间的固定偏置,且柱塞前进;在高速开关高压供油先导阀8的作用下,柱塞腔17与高速开关高压供油阀弹簧腔22沟通时,高速开关高压供油阀在高压油口57的压力作用下打开,因而柱塞腔17的压力接近但略低于高压油口57的压力,柱塞腔17同时与高速开关排油-补油阀弹簧腔沟30通,高速开关排油-补油阀在柱塞腔17的压力作用下保持关闭;(1) State A: high-pressure driving state: during forward rotation, X P < 0, X T > 0, high-speed switching high-pressure oil supply pilot valve 8 displacement is less than negative high-speed switching high-pressure oil supply pilot valve driving bearing 6 and plunger cylinder The fixed offset between the central axes of cylinder 1, the displacement of the high-speed switch oil discharge-oil replenishment pilot valve 9 is greater than the fixed offset between the high-speed switch oil discharge-oil replenishment pilot valve drive bearing 7 and the central axis of the plunger cylinder 1, And the plunger advances; under the action of the high-speed switch high-pressure fuel supply pilot valve 8, when the plunger chamber 17 communicates with the high-speed switch high-pressure fuel supply valve spring chamber 22, the high-speed switch high-pressure fuel supply valve is under the pressure of the high-pressure oil port 57 Open, so the pressure of the plunger chamber 17 is close to but slightly lower than the pressure of the high-pressure oil port 57, the plunger chamber 17 communicates with the spring chamber groove 30 of the high-speed switch oil discharge-replenishment valve at the same time, and the high-speed switch oil discharge-replenishment valve is in the The plunger chamber 17 remains closed under pressure;
(2)状态B,C:空行程状态:其中B为过渡状态,C为补油状态;高速开关高压供油先导阀8位移大于负的高速开关高压供油先导阀驱动轴承6与柱塞缸筒1中心轴线之间的固定偏置,高速开关排油-补油先导阀9位移大于高速开关排油-补油先导阀驱动轴承7与柱塞缸筒1中心轴线之间的固定偏置,且柱塞前进;在高速开关高压供油先导阀8的作用下,高压油口57与高速开关高压供油阀弹簧腔22沟通,高速开关高压供油阀在高压油口57的压力作用下快速关闭,柱塞继续前进导致柱塞腔17体积增加,压力快速降到低于回油口58的背压,柱塞腔17同时与高速开关排油-补油阀弹簧腔30沟通,排油-补油阀在柱塞腔17的压力降低到回油口58背压以下后打开,其中高速开关排油-补油阀打开的过程为过渡状态B;高速开关排油-补油阀打开后柱塞从回油口补油直到到达吸排油分界面的过程为补油状态C;(2) State B, C: Empty travel state: where B is the transition state, and C is the oil supply state; the displacement of the high-speed switch high-pressure oil
(3)状态D:正常回油状态:高速开关高压供油先导阀8位移大于负的高速开关高压供油先导阀驱动轴承6与柱塞缸筒1中心轴线之间的固定偏置,高速开关排油-补油先导阀9位移大于高速开关排油-补油先导阀驱动轴承7与柱塞缸筒1中心轴线之间的固定偏置,且柱塞后退;在高速开关高压供油先导阀8的作用下,高速开关高压供油阀弹簧腔22与高压油口57连通,高压供油阀保持关闭;带背压的回油口58与高速开关排油-补油阀弹簧腔30沟通,由于柱塞排油时,柱塞腔17压力接近并略高于带背压的回油口58压力,故高速开关排油-补油阀在柱塞腔17的压力作用下保持打开状态进行正常回油;(3) State D: normal oil return state: the high-speed switch high-pressure oil
(4)状态E,F:泵输出状态:其中E为过渡状态,F为泵输出状态;高速开关高压供油先导阀8位移大于负的高速开关高压供油先导阀驱动轴承6与柱塞缸筒1中心轴线之间的固定偏置,高速开关排油-补油先导阀9位移小于高速开关排油-补油先导阀驱动轴承7与柱塞缸筒1中心轴线之间的固定偏置,且柱塞后退;在高速开关排油-补油先导阀9的作用下,柱塞腔17与高速开关排油-补油阀弹簧腔30沟通,高速开关排油-补油阀在柱塞腔17的压力作用下关闭,柱塞继续后退导致柱塞腔17体积减小,压力快速上升到超过高压油口57的压力,高压油口57同时与高速开关高压供油阀弹簧腔22沟通,高速开关高压供油阀在柱塞腔17的压力上升到高压油口57压力以上后打开;其中状态E为高速开关高压供油阀开启过程这一过渡状态,状态F为柱塞通过向高压油口57排油直到柱塞转到排吸油分界面。(4) State E, F: pump output state: where E is the transition state, and F is the pump output state; the displacement of the high-speed switch high-pressure oil
最后,需要注意的是,以上列举的仅是本实用新型的具体实施例。显然,本实用新型不限于以上实施例,还能够有很多变形。本领域的普通技术人员能从本实用新型公开的内容中直接导出或联想到的所有变形,均应认为是本实用新型的保护范围。Finally, it should be noted that what is listed above are only specific embodiments of the present invention. Apparently, the utility model is not limited to the above embodiments, and many modifications can be made. All deformations that a person skilled in the art can derive or associate directly from the content disclosed in the utility model shall be considered as the protection scope of the utility model.
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CN101892943B (en) * | 2010-06-04 | 2013-04-24 | 杭州慧翔机电控制工程有限公司 | Switch motor variable-torque oil distribution mechanism capable of independently adjusting oil absorption and extraction and torque shift method |
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