WO2013000321A1 - 一种起重机闭式回转液压系统及起重机 - Google Patents
一种起重机闭式回转液压系统及起重机 Download PDFInfo
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- WO2013000321A1 WO2013000321A1 PCT/CN2012/074212 CN2012074212W WO2013000321A1 WO 2013000321 A1 WO2013000321 A1 WO 2013000321A1 CN 2012074212 W CN2012074212 W CN 2012074212W WO 2013000321 A1 WO2013000321 A1 WO 2013000321A1
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- closed
- crane
- port
- swing
- hydraulic system
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
- B66C23/00—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes
- B66C23/62—Constructional features or details
- B66C23/84—Slewing gear
- B66C23/86—Slewing gear hydraulically actuated
Definitions
- the present invention relates to the field of construction machinery, and more particularly to a closed rotary hydraulic system for a crane.
- the invention also relates to a crane provided with the closed swing hydraulic system.
- a crane is a construction machine that uses a boom to lift a heavy object while working, and then relies on a turntable to transfer the weight from one position to another.
- the slewing mechanism is a device for realizing a slewing movement of the slewing portion of the crane relative to the non-slewing portion.
- the function of the slewing mechanism is to make the upper part of the vehicle rotate around the center of rotation of the crane, and connect the upper and lower vehicles in a rolling support manner.
- the integration makes the load on the vehicle pass to the chassis of the chassis, and its dynamic characteristics directly affect the working characteristics of the entire crane.
- the crane's rotary operation has the characteristics of large moment of inertia, large inertia, and large shock load of the brake.
- the hydraulic system generally has two implementations: open system and closed system:
- the open system means that the hydraulic pump sucks oil from the fuel tank. After the hydraulic oil passes through various control valves, it drives the hydraulic actuators and then flows back to the fuel tank.
- This system has a simple structure and can play the role of heat dissipation and sedimentation of the fuel tank. Due to the commutation shock, and the oil is often in contact with the air, the air is easily infiltrated into the system, resulting in poor stability of the mechanism;
- Closed system means that the oil inlet pipe of the hydraulic pump is directly connected to the oil return pipe of the actuator.
- the hydraulic oil is closed in the pipeline of the system; its compact structure, less chance of contact with air, and the air is not easy to penetrate into the system.
- the commutation shock is reduced, which is beneficial to the stability of the rotation and avoids the hydraulic shock and energy loss that occurs during the commutation of the open system.
- a proportional pump, a cover-type cartridge valve, etc. are usually used to achieve smooth control of the swing.
- the crawler crane rotary closed system disclosed in the utility model patent publication No. CN 201433063Y (see Fig. 1), Includes:
- the utility model also comprises a two-speed valve block 2, wherein the two-speed valve group has an A1 port, a B1 port, an A2 port and a B2 port, and the two-speed valve group further comprises:
- the check valve 21 and the check valve 21 ' are connected in series between the A1 port and the B1 port;
- the two-position four-way reversing valve 22 has a P port connected between the two check valves through a pipeline;
- the third logic cartridge valve wherein the control ports of the first logic cartridge valve 23 and the second logic cartridge valve 24 are both connected to the B port of the 4/2-way reversing valve 22, and the control of the third logic cartridge valve 25
- the port is connected to the port A of the four-way four-way switching valve 22, the port B of the first logic cartridge valve 23 is connected to the port B1, and the port B of the second logic cartridge valve 24 is connected to the port A1,
- the second port of the second logic cartridge valve 24 and the third logic cartridge valve 25 are connected to the A2 port, and the port A of the first logic cartridge valve 23 and the port B of the third logic cartridge valve 25 are connected to the port B2.
- the closed variable pump 1 and at least a certain amount of motors are connected in parallel to the A1 port and the B1 port, and the A2 and B2 ports are connected at least to the A port and the B port of a certain amount of motors.
- the closed system realizes the smooth control of the rotation through the closed variable pump, the two-speed valve group, etc., although the crane can be used to some extent, there is still a certain impact during the start, stop and rotation, and Instantaneous impact due to sudden load changes cannot be avoided.
- the closed system is too complicated, the number of hydraulic pipelines and control components is too large, not only the manufacturing cost is high, but also the maintenance is difficult, there may be more fault points, and the probability of a turning fault is relatively high.
- it is necessary to operate multiple control valves to coordinate the action, which puts high demands on the operator.
- a first object of the present invention is to provide a closed hydraulic system for a crane.
- the hydraulic system has a very reliable and smooth performance during start, stop and turn, and the hydraulic structure is more compact.
- a second object of the present invention is to provide a crane provided with the above-described closed swing hydraulic system.
- the present invention provides a closed hydraulic system for a crane, comprising a closed hydraulic pump and a swing motor, wherein an oil outlet of the closed hydraulic pump is connected to an oil inlet of the swing motor.
- the oil outlet of the swing motor is connected to the oil inlet of the closed hydraulic pump, and further comprising buffer damping, the buffer damping and the swing motor being on the hydraulic oil circuit Parallel.
- the damping diameter of the damping damping matches the displacement of the closed hydraulic pump and the swing motor.
- the control oil passage of the brake of the swing motor is provided with a two-position four-way reversing valve and a pressure reducing valve
- the P port of the two-position four-way reversing valve is a control oil inlet port and an A port.
- the P port connected to the pressure reducing valve is a cut-off port
- the T port is connected to the oil tank
- the A port of the pressure reducing valve is connected to the oil inlet of the brake.
- the pressure reducing valve is connected in parallel with a one-way valve that allows hydraulic oil to flow from the brake to the port of the two-position four-way switching valve A, and the pressure reducing valve and the one-way valve constitute a one-way pressure reducing valve .
- a fixed damping is provided between the pressure relief oil passage of the swing motor and the oil inlet passage of the brake.
- the fixed damped orifice diameter ranges from 0.3 mm to 1. 5 mm.
- the closed hydraulic pump is a closed electric proportional pump.
- the present invention also provides a crane comprising a crane main body, a swing mechanism, and a swing hydraulic system, the swing hydraulic system being specifically the crane closed swing hydraulic system according to any one of the above.
- the closed swing hydraulic system of the crane provided by the present invention comprises a closed hydraulic pump, a swing motor and a buffer damping, and an oil outlet of the closed hydraulic pump is connected to an oil inlet of the swing motor, and the swing motor is The oil outlet is connected to the oil inlet of the closed hydraulic pump, and the buffer damping is paralleled with the swing motor on the hydraulic oil circuit.
- the buffer damping Through the buffer damping, the main oil passages at both ends of the swing motor are penetrated.
- a small amount of pressure oil can be unloaded to the other end of the swing motor through the buffer damping, so that the rotation is smoothly started, and the inertia is generated by the buffer damping when the swing is stopped.
- the invention Compared with the existing closed hydraulic system of the crane, the invention only needs a buffer damping to achieve smooth running of the starting, stopping and turning processes, so that the entire hydraulic system is maximized, and the number of components is relatively high. Less, can significantly reduce manufacturing costs, maintenance difficulty, failure probability and operational requirements, making hydraulic piping connections more compact, not only reduces installation space, but also reduces leakage and pipeline vibration caused by pipeline connections, and improves System reliability, cylinder The operation process has been verified, and the test results have proved that the rotation effect is very ideal, which can effectively avoid the turning failure and ensure the safety of man and machine.
- the crane provided by the present invention is provided with the closed hydraulic system of the above-mentioned crane. Since the above-mentioned closed hydraulic system of the crane has the above technical effects, the crane having the closed hydraulic system of the crane should also have corresponding technical effects.
- FIG. 1 is a hydraulic schematic diagram of a crawler closed system of a crawler crane in the prior art
- FIG. 2 is a hydraulic schematic diagram of a closed hydraulic hydraulic system of a crane provided by the present invention.
- the core of the invention is to provide a closed hydraulic hydraulic system for a crane.
- the hydraulic system has a very reliable and smooth performance during start-up, stop and revolving, and the hydraulic structure is relatively simple.
- FIG. 2 is a hydraulic principle diagram of the closed hydraulic system of the crane provided by the present invention.
- the crane closed hydraulic system of the present invention comprises a closed hydraulic pump 10 and a swing motor 20, and the oil outlet of the closed hydraulic pump 10 is connected to the oil inlet of the swing motor 20, and is rotated.
- the oil outlet of the motor 20 is connected to the oil inlet of the closed hydraulic pump 10 to form a closed hydraulic circuit, that is, a closed hydraulic system.
- the closed hydraulic pump 10 can adopt a closed electric proportional pump, and its flow rate can be steplessly adjusted within the range of 0-100%, without the need for a reversing valve, and the flow rate and direction of the hydraulic oil in the main oil passage can be changed by the variable of the pump.
- the shifting and reversing of the swing motor 20 is excellent in fretting and stable operation.
- a damping damping 30 is further provided. One end of the damping damping 30 is connected to the oil inlet of the swing motor 20, and the other end is connected to the oil outlet of the swing motor 20. That is, the damper damping 30 is connected in parallel with the slewing motor 20 on the hydraulic oil line.
- the diameter of the damper hole of the damper damping 30 is matched with the displacement of the closed hydraulic pump 10 and the slewing motor 20. If the diameter of the damper hole is too large, excessive hydraulic oil flows from the high pressure end to the low pressure end of the slewing motor 20, and The swing motor cannot be normally driven. If the diameter of the orifice is too small, only a very small amount of hydraulic oil flows from the high pressure end to the low pressure end of the swing motor 20, and the unloading action cannot be performed.
- the slewing motor 20 is provided with a parking brake 40.
- the brake cylinder of the brake 40 is normally closed, that is, the slewing motor 20 is restricted by the action of the spring force when not operating, and only the pressure oil enters the brake cylinder, and the reverse force overcomes the spring force. The role can be released.
- the control oil passage (dashed line part) of the brake 40 is provided with a reversing valve and a pressure reducing valve 60.
- a two-position four-way reversing valve 50 is adopted, and the P port is a control oil inlet port, and the A port connection is reduced.
- the oil inlet of the pressure valve 60, the B port is a cut-off port, the T port is connected to the oil tank, and the oil outlet of the pressure reducing valve 60 is connected to the oil inlet of the brake 40.
- the pressure reducing valve 60 has a one-way valve 70 in parallel, and the one-way valve 70 constitutes a one-way pressure reducing valve. This one-way valve 70 only allows hydraulic oil to flow from the brake 40 to the A port of the four-way four-way switching valve 50.
- a fixed damping 80 is provided, and the diameter of the damper hole of the fixed damping 80 can be controlled between 0.3 mm and 1. 5 mm.
- the closed electric proportional pump 10 of the present invention is connected to the two pressure ports of the swing motor 20, and the control oil is opened by the proportional pressure reducing valve 60, and the effective buffer of the damping damping 30 is used to operate the electronically controlled rotary handle to control the closed electric proportional pump.
- the proportional current output of 10 can realize smooth start of swing, stable stop of rotation, smooth and free slip in the process of rotation.
- the specific working process is as follows:
- the buffer damping 30 can effectively filter the peak pressure by timely unloading a small amount of pressure oil, thereby avoiding the instantaneous impact caused by the sudden change of the load, thereby ensuring the smooth operation of the crane during the turning process.
- the rotary electric control handle When the sling is to be freely slid, the rotary electric control handle does not need to be operated, and only the two-position four-way directional control valve 50 is energized. At this time, the oil is buffer damped 30 from the slewing motor 20 due to the action of the eccentric load. One end unloads to the other end, thereby achieving free slip, and the probability of failure is small.
- the present invention can unload a little pressure oil to the other end of the swing motor 20 through the buffer damping 30, so that the rotation can be smoothly started; when the swing stops, the inertia generated pressure oil can be partially unloaded to the swing motor 20 by the buffer damping 30.
- the rotation is stopped smoothly; during the rotation process, the peak pressure can be filtered by the damping damping 30, so that the rotation process is smooth; when the lifting weight is to be centered, the free sliding can be realized by the buffer damping 30.
- the invention Compared with the existing closed hydraulic system of the crane, the invention only needs a buffer damping 30 to achieve smooth running of the starting, stopping and turning processes, thereby maximizing the overall hydraulic system, and the number of components thereof. Less, it can significantly reduce manufacturing costs, maintenance difficulty, failure probability and operational requirements, making hydraulic piping connections more compact, not only reducing installation space, but also reducing leakage and pipeline vibration caused by pipeline connections, improving The reliability of the system, the operation process is completed, and the test results prove that the rotation effect is very ideal, which can effectively avoid the turning failure and ensure the safety of man and machine.
- the above closed hydraulic system of the crane is only a preferred solution, and its specific structure is not On this basis, based on this, a targeted adjustment can be made according to actual needs, thereby obtaining different implementation manners.
- other types of reversing valves are used instead of the four-way four-way reversing valve to perform the reversing function, as long as the brake action can be controlled in the set flow direction.
- the present invention also provides a crane including a crane main body, a swing mechanism and a swing hydraulic system, and the swing hydraulic system is specifically the above-mentioned crane closed swing hydraulic system, and the rest of the structure is requested. Referring to the prior art, this article will not repeat them.
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Abstract
本发明公开了一种起重机闭式回转液压系统，包括闭式液压泵（10）和回转马达（20），所述闭式液压泵（10）的出油口与所述回转马达（20）的进油口相连，所述回转马达（20）的出油口与所述闭式液压泵（10）的进油口相连，其特征在于，进一步包括缓冲阻尼（30），所述缓冲阻尼（30）与回转马达（20）在液压油路上相并联。该液压系统在启动、停止以及回转过程中具有十分可靠的平稳性能，而且液压结构较为简单。本发明还公开了设有所述起重机闭式回转液压系统的起重机。
Description
一种起重机闭式回转' ½系统^重机 本申请要求于 2011 年 06 月 29 日提交中国专利局、 申请号为 201110179255.5、 发明名称为"一种起重机闭式回转液压系统及起重机"的 中国专利申请的优先权， 其全部内容通过引用结合在本申请中。
技术领域
本发明涉及工程机械技术领域， 特别是涉及起重机的闭式回转液压系 统。 本发明还涉及设有所述闭式回转液压系统的起重机。
背景技术
起重机是一种在工作时利用起重臂吊起重物， 然后依靠转台回转将重 物从一个位置转移至另外一个位置的工程机械。
回转机构是起重机的回转部分相对于非回转部分实现回转运动的装 置， 回转机构的作用是使上车部分绕起重机的回转中心做回转运动， 并以 滚动支撑的方式将上车和下车连成一体，使上车的载荷传递到底盘车架上， 其动态特性直接影响整个起重机的工作特性。
起重机回转作业具有转动惯量大、惯性大、启制动沖击载荷大等特点， 其液压系统一般有开式系统和闭式系统两种实现方式：
开式系统是指液压泵从油箱吸油， 液压油经各种控制阀后， 驱动液压 执行元件， 然后流回油箱， 这种系统结构较为简单， 可以发挥油箱的散热、 沉淀杂质作用。 由于存在换向冲击， 且油液常与空气接触， 使空气易于渗 入系统， 导致机构的回转稳定性差；
闭式系统是指液压泵的进油管直接与执行元件的回油管相连， 液压油 在系统的管路中进行封闭循环； 其结构紧凑， 与空气接触机会少， 空气不 易渗入系统， 由于不含换向阀， 减少了换向沖击， 有利于实现回转的稳定 性， 避免了开式系统换向过程中所出现的液压沖击和能量损失。
在闭式系统中， 通常采用比例泵、 盖板式插装阀等实现回转的平稳控 制， 如授权公告号为 CN 201433063Y的实用新型专利说明书公开的履带起 重机回转闭式系统 （见图 1 ), 包括：
闭式变量泵 1 ;
至少两定量马达， 依次为第一定量马达 3、 第二定量马达 4、 第三定量 马达 5; 替换页 （细则第 26条)
还包括二速阀组 2 , 该二速阀组有 A1 口、 B1 口、 A2口和 B2口， 该二 速阀组还包括：
单向阀 21和单向阀 21 ' , 相背串联于 A1口和 B 1口之间；
二位四通换向阀 22 , 其 P口通过管路连接于两单向阀之间；
三逻辑插装阀， 其中， 第一逻辑插装阀 23和第二逻辑插装阀 24的控 制口均连接于二位四通换向阀 22的 B口， 第三逻辑插装阀 25的控制口连 接于二位四通换向阀 22的 A口， 第一逻辑插装阀 23的 B口连接于所述 B1 口， 第二逻辑插装阀 24的 B口连接于所述 A1口， 第二逻辑插装阀 24和第 三逻辑插装阀 25的 A口相连接于 A2口 ,第一逻辑插装阀 23的 A口和第三 逻辑插装阀 25的 B口相连于 B2口， 所述闭式变量泵 1和至少一定量马达 并联后连接于 A1口和 B1口， 所述 A2、 B2口至少与一定量马达的 A口和 B 口相应连接。
该闭式系统通过闭式变量泵、 二速阀组等实现回转的平稳控制， 虽然 能在一定程度上满足起重机的使用要求， 但在启动、 停止及回转过程中仍 存在一定的沖击， 且无法避免因负载突变所造成的瞬时沖击。
此外， 该闭式系统过于复杂， 液压管路和控制元器件数量太多， 不仅 制造成本较高， 且维护难度较大， 可能存在的故障点较多， 出现回转故障 的几率相对较高， 在进行自由滑转时， 需要操作多个控制阀协调动作， 对 操作人员提出了较高要求。
因此， 如何通过较为筒单的方式来提高起重机闭式回转液压系统的平 稳性， 是本领域技术人员目前需要解决的技术问题。
发明内容
本发明的第一目的是提供一种起重机闭式回转液压系统。 该液压系统 在启动、 停止以及回转过程中具有十分可靠的平稳性能， 而且液压结构较 为筒单。
本发明的第二目的是提供一种设有上述闭式回转液压系统的起重机。 为了实现上述第一目的， 本发明提供一种起重机闭式回转液压系统， 包括闭式液压泵和回转马达， 所述闭式液压泵的出油口与所述回转马达的 进油口相连， 所述回转马达的出油口与所述闭式液压泵的进油口相连， 其 特征在于， 进一步包括緩沖阻尼， 所述緩沖阻尼与回转马达在液压油路上
相并联。
优选地， 所述緩沖阻尼的阻尼孔直径与所述闭式液压泵和回转马达的 排量相匹配。
优选地， 所述回转马达的制动器的控制油路上设有二位四通换向阀和 减压阀， 所述二位四通换向阀的 P油口为控制油进油口、 A油口连接所述 减压阀的 P油口、 B油口为截止油口、 T油口连接回油油箱， 所述减压阀的 A油口连接所述制动器的进油口。
优选地， 所述减压阀并联有允许液压油从所述制动器流向所述二位四 通换向阀 A油口的单向阀， 所述减压阀与单向阀组成单向减压阀。
优选地， 所述回转马达的卸压油路与所述制动器的进油油路之间设有 固定阻尼。
优选地， 所述固定阻尼的阻尼孔直径范围在 0. 3mm- 1. 5mm之间。
优选地， 所述闭式液压泵为闭式电比例泵。
为了实现上述第二目的，本发明还提供一种起重机， 包括起重机主体、 回转机构以及回转液压系统， 所述回转液压系统具体为上述任一项所述的 起重机闭式回转液压系统。
本发明所提供的起重机闭式回转液压系统， 包括闭式液压泵、 回转马 达以及緩沖阻尼，所述闭式液压泵的出油口与所述回转马达的进油口相连， 所述回转马达的出油口与所述闭式液压泵的进油口相连， 所述緩沖阻尼与 回转马达在液压油路上相并联。 通过緩沖阻尼将回转马达两端的主油路贯 通， 回转启动时， 通过緩沖阻尼可将少许压力油卸荷至回转马达另一端， 使得回转平稳地启动， 回转停止时， 通过緩沖阻尼可将惯性产生的压力油 部分卸荷至回转马达另一端， 使得回转平稳地停止， 回转进行过程中， 通 过緩沖阻尼可过滤尖峰压力， 使得回转过程平稳， 吊重须对中时， 通过緩 沖阻尼即可实现自由滑转。
与现有起重机闭式回转液压系统相比， 本发明只需一个緩沖阻尼即可 实现启动、 停止及回转过程的平稳运行， 从而使整个液压系统得到了最大 程度的筒化， 其元器件数量较少， 可显著降低制造成本、 维护难度、 故障 几率和操作要求， 使液压管路连接变得更加筒单， 不仅缩小了安装空间， 而且减少了由管路连接造成的泄漏和管道振动， 提高了系统的可靠性， 筒
化了操作过程， 经试验验证， 回转效果十分理想， 可有效避免回转故障， 确保人机安全。
本发明所提供的起重机设有上述起重机闭式回转液压系统， 由于上述 起重机闭式回转液压系统具有上述技术效果， 具有该起重机闭式回转液压 系统的起重机也应具备相应的技术效果。
附图说明
图 1为现有技术中一种履带起重机回转闭式系统的液压原理图； 图 2为本发明所提供起重机闭式回转液压系统的液压原理图。
图 1中：
1.闭式变量泵 2.二速阀组 3.第一定量马达 4.第二定量马达
5.第三定量马达 21、 IV ·单向阀 22.二位四通换向阀 23.第一逻 辑插装阀 24.第二逻辑插装阀 25.第三逻辑插装阀
图 2中：
10.闭式液压泵 20.回转马达 30.緩沖阻尼 40.制动器 50. 二位四通换向阀 60.减压阀 70.单向阀 80.固定阻尼
具体实施方式
本发明的核心在于提供一种起重机闭式回转液压系统。 该液压系统在 启动、 停止以及回转过程中具有十分可靠的平稳性能， 而且液压结构较为 筒单。
为了使本技术领域的人员更好地理解本发明方案， 下面结合附图和具 体实施方式对本发明作进一步的详细说明。
请参考图 2 , 图 2为本发明所提供起重机闭式回转液压系统的液压原 理图。
在一种具体实施方式中， 本发明提供的起重机闭式回转液压系统， 包 括闭式液压泵 10和回转马达 20 , 闭式液压泵 10的出油口与回转马达 20 的进油口相连， 回转马达 20的出油口与闭式液压泵 10的进油口相连， 形 成封闭的液压油路， 即闭式液压系统。
闭式液压泵 10可采用闭式电比例泵， 其流量可以在 0-100%范围内无 级调节， 无需换向阀， 通过泵的变量改变主油路中液压油的流量和方向， 来实现回转马达 20的变速和换向， 其微动性好， 且工作平稳。
为提高液压系统在启动、 停止以及回转过程中的平稳性， 这里进一步 设有緩沖阻尼 30 , 緩沖阻尼 30的一端与回转马达 20的进油口连通， 另一 端与回转马达 20的出油口连通，即緩沖阻尼 30与回转马达 20在液压油路 上相并联。
緩沖阻尼 30的阻尼孔直径与闭式液压泵 10和回转马达 20的排量相匹 配，若阻尼孔的直径过大， 则会有过量的液压油从回转马达 20的高压端流 向低压端， 而无法正常驱动回转马达， 若阻尼孔的直径过小， 则仅有极微 量的液压油从回转马达 20的高压端流向低压端， 无法起到卸荷的作用。
回转马达 20设有停车制动器 40 , 该制动器 40的制动油缸为常闭式， 即不动作时依靠弹簧力的作用限制回转马达 20运行，只有压力油进入制动 油缸， 反向克服弹簧力的作用才能解除制动。
制动器 40的控制油路（虚线部分）上设有换向阀和减压阀 60 , 这里 采用了二位四通换向阀 50 , 其 P油口为控制油进油口， A油口连接减压阀 60的进油口， B油口为截止油口， T油口连接油箱， 减压阀 60的出油口连 接制动器 40的进油口。
减压阀 60并联有单向阀 70 , 与单向阀 70组成单向减压阀， 此单向阀 70仅允许液压油从制动器 40流向二位四通换向阀 50的 A油口。
解除制动时，二位四通换向阀 50的右位工作，其 P油口与 A油口连通， T油口与 B油口连通， 液压油经过其 P油口、 A油口以及减压阀 60的 P油 口、 A油口进入制动器 40的制动油缸， 克服弹簧力的作用解除制动。
制动时， 二位四通换向阀 50的左位工作， 其 P油口与 B油口连通， A 油口与 T油口连通，制动油缸中的液压油经单向阀 70、 二位四通换向阀 50 的 A油口、 T油口返回油箱， 制动器 40的弹簧复位， 进入制动状态。
回转马达 20 的卸压油路与制动器 40 的进油油路之间设有固定阻尼 80 , 固定阻尼 80的阻尼孔直径范围可控制在 0. 3mm- 1. 5mm之间。
本发明的闭式电比例泵 10连接回转马达 20的两压力油口， 控制油经 比例减压阀 60将制动器打开， 借助緩沖阻尼 30的有效緩沖， 操作电控回 转手柄控制闭式电比例泵 10的比例电流输出， 可实现回转启动平稳、 回转 停止平稳、 回转过程中平稳以及自由滑转， 其具体工作过程如下：
1 ) 回转启动平稳
回转启动时， 通过操作回转电控手柄， 使闭式电比例泵 10的排量由零 緩慢增大， 驱动回转马达 20动作， 压力油有少许从緩沖阻尼 30卸荷至回 转马达 20另一端， 避免了回转启动时压力突然增大造成沖击， 使回转平稳 地启动。
2 ) 回转停止平稳
回转停止时， 通过操作回转电控手柄， 使闭式电比例泵 10的排量由较 大緩慢减为零， 此时压力油有少许从緩沖阻尼 30卸荷至回转马达 20另一 端， 避免了因停止时的惯性影响造成压力突然增大， 从而避免了停止时产 生沖击， 使回转平稳地停止。
3 ) 回转过程中平稳
回转过程中， 当负载突变时， 緩沖阻尼 30通过及时卸荷少许压力油， 可有效过滤尖峰压力， 避免因负载突变所造成的瞬时沖击， 从而保证回转 过程中起重机能平稳作业。
4 ) 自由滑转
吊重对中须自由滑转时， 不须操作回转电控手柄， 只需二位四通换向 阀 50得电， 此时由于偏载的作用， 使油液经緩沖阻尼 30从回转马达 20 一端卸荷至另一端， 从而实现自由滑转， 故障几率小。
可见， 本发明通过緩沖阻尼 30可将少许压力油卸荷至回转马达 20另 一端， 使得回转平稳地启动； 回转停止时， 通过緩沖阻尼 30可将惯性产生 的压力油部分卸荷至回转马达 20另一端，使得回转平稳地停止； 回转进行 过程中， 通过緩沖阻尼 30可过滤尖峰压力， 使得回转过程平稳； 吊重须对 中时， 通过緩沖阻尼 30即可实现自由滑转。
与现有起重机闭式回转液压系统相比， 本发明只需一个緩沖阻尼 30 即可实现启动、 停止及回转过程的平稳运行， 从而使整个液压系统得到了 最大程度的筒化， 其元器件数量较少， 可显著降低制造成本、 维护难度、 故障几率和操作要求， 使液压管路连接变得更加筒单， 不仅缩小了安装空 间， 而且减少了由管路连接造成的泄漏和管道振动，提高了系统的可靠性， 筒化了操作过程， 经试验验证， 回转效果十分理想， 可有效避免回转故障， 确保人机安全。
上述起重机闭式回转液压系统仅是一种优选方案， 其具体结构并不局
限于此， 在此基础上可根据实际需要作出具有针对性的调整， 从而得到不 同的实施方式。 例如采用其它类型的换向阀取代二位四通换向阀来执行换 向功能， 只要能够按设定的流向控制制动器动作即可。
除了上述起重机闭式回转液压系统， 本发明还提供了一种起重机， 包 括起重机主体、 回转机构以及回转液压系统， 所述回转液压系统具体为以 上所述的起重机闭式回转液压系统， 其余结构请参考现有技术， 本文不再 赘述。
以上对本发明所提供的起重机闭式回转液压系统及起重机进行了详细 上实施例的说明只是用于帮助理解本发明的核心思想。 应当指出， 对于本 技术领域的普通技术人员来说， 在不脱离本发明原理的前提下， 还可以对 本发明进行若干改进和修饰， 这些改进和修饰也落入本发明权利要求的保 护范围内。
Claims
1、 一种起重机闭式回转液压系统， 包括闭式液压泵（ 10 )和回转马达 (20), 所述闭式液压泵（10)的出油口与所述回转马达（20)的进油口相 连， 所述回转马达（20)的出油口与所述闭式液压泵（10)的进油口相连， 其特征在于， 进一步包括緩沖阻尼（ 30 ), 所述緩沖阻尼（ 30 )与回转马达 ( 20 )在液压油路上相并联。
2、根据权利要求 1所述的起重机闭式回转液压系统， 其特征在于， 所 述緩沖阻尼（ 30 )的阻尼孔直径与所述闭式液压泵（ 10 )和回转马达（ 20 ) 的排量相匹配。
3、根据权利要求 1至 2任一项所述的起重机闭式回转液压系统，其特 征在于， 所述回转马达（20) 的制动器（40) 的控制油路上设有二位四通 换向阀 （50)和减压阀 （60), 所述二位四通换向阀 （50)的 P油口为控制 油进油口、 A油口连接所述减压阀 （ 60 ) 的 P油口、 B油口为截止油口、 T 油口连接回油油箱， 所述减压阀 （60) 的 A油口连接所述制动器（40) 的 进油口。
4、根据权利要求 3所述的起重机闭式回转液压系统， 其特征在于， 所 述减压阀 （60)并联有允许液压油从所述制动器（40) 流向所述二位四通 换向阀 （50) A油口的单向阀 0), 所述减压阀 （60)与单向阀 （70)组 成单向减压阀。
5、根据权利要求 4所述的起重机闭式回转液压系统， 其特征在于， 所 述回转马达（20) 的卸压油路与所述制动器（40) 的进油油路之间设有固 定阻尼（80)。
6、根据权利要求 5所述的起重机闭式回转液压系统， 其特征在于， 所 述固定阻尼（ 80 ) 的阻尼孔直径范围在 0.3mm- 1.5mm之间。
7、根据权利要求 6所述的起重机闭式回转液压系统， 其特征在于， 所 述闭式液压泵（10) 为闭式电比例泵。
8、 一种起重机， 包括起重机主体、 回转机构以及回转液压系统， 其特 征在于， 所述回转液压系统具体为上述权利要求 1至 7任一项所述的起重 机闭式回转液压系统。
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| CN102229416B (zh) * | 2011-06-29 | 2013-06-05 | 三一汽车起重机械有限公司 | 一种起重机闭式回转液压系统及起重机 |
| CN102602830B (zh) * | 2012-03-06 | 2013-11-20 | 中联重科股份有限公司 | 一种液压回转系统及工程车辆 |
| CN102730582B (zh) * | 2012-06-20 | 2014-12-17 | 上海三一科技有限公司 | 一种液压回转系统启停缓冲装置及起重机 |
| CN102865262B (zh) * | 2012-09-07 | 2015-10-28 | 三一重工股份有限公司 | 回转液压系统及工程机械 |
| CN102877783B (zh) * | 2012-09-28 | 2014-10-15 | 三一重工股份有限公司 | 旋挖钻机及其回转液压系统 |
| CN103523686B (zh) * | 2013-11-01 | 2015-05-20 | 太原重工股份有限公司 | 大型移动式起重机 |
| CN103723632B (zh) * | 2013-12-13 | 2016-06-08 | 中联重科股份有限公司 | 起重机的回转控制方法、回转控制系统及起重机 |
| CN105439018B (zh) * | 2014-11-26 | 2018-02-16 | 徐州重型机械有限公司 | 具有分段控制功能的回转液控系统及起重机 |
| CN105156392B (zh) * | 2015-09-23 | 2017-12-15 | 武汉船用机械有限责任公司 | 一种管路加热放气阀及起重机的回转闭式液压系统 |
| CN105351276B (zh) * | 2015-12-03 | 2017-09-19 | 徐州重型机械有限公司 | 回转液压控制系统、方法及起重机 |
| CN106681238A (zh) * | 2017-03-15 | 2017-05-17 | 天空概念（北京）防务科技有限公司 | 一种回转机构控制电路及控制方法 |
| CN107169254B (zh) * | 2017-07-21 | 2020-04-28 | 济南大学 | 一种汽车起重机回转系统性能评估及剩余寿命预测方法 |
| CN107740747A (zh) * | 2017-10-13 | 2018-02-27 | 三汽车起重机械有限公司 | 限速液压马达、起重机以及马达转速的控制方法 |
| CN111734696B (zh) * | 2020-07-02 | 2022-04-08 | 浙江中液机械设备有限公司 | 一种基于闭环控制的闭式液压系统及控制方法 |
| CN119954051B (zh) * | 2025-03-06 | 2025-10-17 | 浙江三一装备有限公司 | 闭式回转液压系统、起重设备及闭式回转控制方法 |
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