WO2011127807A1 - 液压控制系统和液压控制方法 - Google Patents

液压控制系统和液压控制方法 Download PDF

Info

Publication number
WO2011127807A1
WO2011127807A1 PCT/CN2011/072627 CN2011072627W WO2011127807A1 WO 2011127807 A1 WO2011127807 A1 WO 2011127807A1 CN 2011072627 W CN2011072627 W CN 2011072627W WO 2011127807 A1 WO2011127807 A1 WO 2011127807A1
Authority
WO
WIPO (PCT)
Prior art keywords
engine
closed pump
hydraulic
hydraulic control
pump
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2011/072627
Other languages
English (en)
French (fr)
Inventor
詹纯新
刘权
张源
宋春阳
王少军
袁知华
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hunan Zoomlion Special Vehicle Co Ltd
Changsha Zoomlion Heavy Industry Science and Technology Development Co Ltd
Original Assignee
Hunan Zoomlion Special Vehicle Co Ltd
Changsha Zoomlion Heavy Industry Science and Technology Development Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hunan Zoomlion Special Vehicle Co Ltd, Changsha Zoomlion Heavy Industry Science and Technology Development Co Ltd filed Critical Hunan Zoomlion Special Vehicle Co Ltd
Priority to US13/641,096 priority Critical patent/US20130091833A1/en
Publication of WO2011127807A1 publication Critical patent/WO2011127807A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/18—Combined units comprising both motor and pump
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
    • B60W10/00—Conjoint control of vehicle sub-units of different type or different function
    • B60W10/04—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units
    • B60W10/06—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units including control of combustion engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/005—With rotary or crank input
    • F15B7/006—Rotary pump input
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/44—Control of exclusively fluid gearing hydrostatic with more than one pump or motor in operation
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K5/00—Arrangement or mounting of internal-combustion or jet-propulsion units
    • B60K5/08—Arrangement or mounting of internal-combustion or jet-propulsion units comprising more than one engine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20561—Type of pump reversible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20569—Type of pump capable of working as pump and motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/27—Directional control by means of the pressure source
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/76—Control of force or torque of the output member
    • F15B2211/761—Control of a negative load, i.e. of a load generating hydraulic energy
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/76—Control of force or torque of the output member
    • F15B2211/763—Control of torque of the output member by means of a variable capacity motor, i.e. by a secondary control on the motor

Definitions

  • the present invention relates to the field of hydraulic technology, and in particular to a hydraulic control system and a hydraulic control method.
  • hydraulic control systems mainly include open systems and closed systems, specifically, open systems and single pumps including parallel pumps in parallel.
  • hydraulic control systems mainly include open systems and closed systems, specifically, open systems and single pumps including parallel pumps in parallel.
  • closed control system Since the single-pump-driven closed control system is driven by a single pump, the single-pump engine must meet the needs of large-tonnage cranes and is therefore limited in terms of selection.
  • An object of the present invention is to provide a hydraulic control system and a hydraulic control method for solving the problem that the engine selection of the hydraulic control system in the prior art is large, or the system has complicated pipelines, large heat generation, and many fault sources. The startup performance of the action is not ideal.
  • a hydraulic control system comprises: a first closed pump and a first engine connected to each other; a second closed pump and a second engine connected to each other; a hydraulic motor; wherein the first closed pump and the second closed The pump is connected in parallel with the hydraulic motor.
  • the hydraulic control system of the present invention further includes a brake coupled to the output of the hydraulic motor.
  • the hydraulic control system of the present invention further includes a controller coupled to the first engine and the second engine, the controller for activating the first engine and the second engine, and further for When the first closed pump or the second closed pump fails, the first engine or the second engine is stopped accordingly.
  • the controller is further configured to detect a rotation speed of the first engine and the second engine and calculate a difference between the two; if the difference is greater than a preset value, if the current job is a rising operation, Then, the engine speed of the engine with a lower rotation speed is increased; if the current operation is a lowering operation, the displacement of the pump corresponding to the engine with a higher rotation speed is reduced.
  • the controller is connected to the first closed pump, the second closed pump and the hydraulic motor for detecting the rotational speed of the hydraulic motor; adjusting the first closed pump and the second closed pump The displacement of the hydraulic motor is set to a preset value.
  • the hydraulic control method of the present invention is applied to the hydraulic control system of the present invention, the method comprising: when the first closed pump or the second closed pump fails, respectively stopping the first engine or the second engine.
  • yet another hydraulic control method is provided.
  • the hydraulic control method of the present invention is applied to the hydraulic control system of the present invention, the method comprising: detecting a rotational speed of a first engine and a second engine in the hydraulic control system and calculating a difference between the two; When the value is greater than the preset value, if the current job is a rising operation, the engine speed of the engine having a lower rotation speed is increased; and if the current operation is a lowering operation, the displacement of the pump corresponding to the engine having a higher rotation speed is decreased. Further, the method further includes: detecting a rotational speed of the hydraulic motor; adjusting a displacement of the first closed pump and the second closed pump such that a rotational speed of the hydraulic motor is a preset value.
  • yet another hydraulic control method is provided.
  • the hydraulic control method of the present invention is applied to the hydraulic control system of the present invention, the method comprising: detecting the rotational speed of the hydraulic motor; adjusting the amount of the first closed pump and the second closed pump to increase the rotational speed of the hydraulic motor Is the default value.
  • Fig. 1 is a schematic view showing the structure of a hydraulic control system in an embodiment of the present invention.
  • DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS It should be noted that the embodiments in the present application and the features in the embodiments may be combined with each other without conflict. The invention will be described in detail below with reference to the drawings in conjunction with the embodiments.
  • FIG. 1 is a schematic illustration of the construction of a hydraulic control system in an embodiment of the invention.
  • the hydraulic control system in the embodiment of the present invention mainly includes a first engine M1 and a first closed pump P1, a second engine M2 connected thereto, and a second closed pump P2 connected thereto, and a hydraulic pressure.
  • Motor P3 serves as an actuator.
  • the first closed pump P1, the second closed pump P2 and the hydraulic motor P3 are connected in parallel, that is, the high pressure port A1 of the first closed type pump P1, the high pressure port A2 of the second closed type pump P2, and the A port of the hydraulic motor P3 are mutually connected.
  • the connection port of the first closed pump P1, the pressure port B2 of the second closed pump P2, and the B port of the hydraulic motor P3 are connected to each other.
  • the hydraulic control system in this embodiment may also include a brake 12 to effect braking of the movement of the load 13.
  • the hydraulic control system in this embodiment may further include a controller 11 that can use an existing control device such as a programmable logic controller PLC.
  • the controller 11 is connected to the first engine M1 and the second engine M2 for controlling the rotational speeds of the two engines, thereby realizing the control of the output torque of the two engines, and realizing the starting of the two engines. And stop control.
  • the hydraulic control method in the present embodiment will be described below.
  • the hydraulic control method can be implemented using an existing control device such as a PLC.
  • the controller may detect the rotational speeds of the first engine M1 and the second engine M2 and calculate the difference between the two. If the difference is greater than the preset range, then: if the current job is a rising operation, the engine speed of the engine is increased, and if the current operation is a lowering operation, the row of the pump corresponding to the engine with a higher speed is decreased. Therefore, the output power of the closed pump is controlled within an allowable range, for example, the rotation speed of the second engine M2 is higher, and the displacement of the second closed pump P2 is decreased.
  • the preset range of the difference can be determined by trial-and-risk.
  • the ascending and descending operations here refer to the crane lifting the load from a low position to a high position, respectively, and placing the load from a high position to a low position.
  • the controller 11 can detect the rotational speed of the hydraulic motor P3 and adjust the displacement of the first closed pump P1 and the second closed pump P2 so that the rotational speed of the hydraulic motor P3 is preset. value.
  • the load movement speed can be observed by the operator of the crane and then the rotation speed of the hydraulic motor is set to a preset value by the operation of the joystick 10, and the movement speed of the load at this time also meets the operation requirements.
  • the first engine M1 or the second engine M2 is stopped by the controller 11, correspondingly only by the second engine M2 or the first engine M1. jobs.
  • the first engine M1 and the second engine M2 form a mutual standby relationship, thereby improving the reliability of the system.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Transportation (AREA)
  • Fluid-Pressure Circuits (AREA)

Description

¾ £控制系统和液压控制方法 技术领域 本发明涉及液压技术领域， 具体而言， 涉及一种液压控制系统和液压控 制方法。 背景技术 随着经济的发展， 在生产建设中超大吨位起重机得到了广泛应用， 其中 的液压控制系统主要包括开式系统和闭式系统， 具体而言， 包括双泵并联的 开式系统和单泵驱动的闭式控制系统。 单泵驱动的闭式控制系统由于仅由单泵进行驱动， 该单泵的发动机必须 满足大吨位起重机的需要， 因此在选型方面受到局限。 而对于双泵并联的开 式系统来说， 虽然可以解决超大吨位发动机选型困难的问题， 但是开式系统 管路复杂、 发热量大、 故障源多， 所以动作的微动性能不够理想。 在相关的技术方案中， 液压控制系统的发动机选型局限性较大， 或者系 统的管路复杂、 发热量大、 故障源多、 动作的微动性能不够理想， 针对这些 问题， 目前尚未提出有效的解决方案。 发明内容 本发明的目的在于提供一种液压控制系统和液压控制方法， 以解决现有 技术中液压控制系统的发动机选型局限性较大， 或系统的管路复杂、 发热量 大、 故障源多、 动作的啟动性能不够理想的问题。 为了实现上述目的，才艮据本发明的一个方面，提供了一种液压控制系统。 本发明的液压控制系统包括： 相互连接的第一闭式泵和第一发动机； 相 互连接的第二闭式泵和第二发动机； 液压马达； 其中， 所述第一闭式泵、 第 二闭式泵和所述液压马达并联。 进一步地， 本发明的液压控制系统还包括制动器， 连接在所述液压马达 的输出端。 进一步地， 本发明的液压控制系统还包括与所述第一发动机和所述第二 发动机连接的控制器， 该控制器用于启动所述第一发动机和第二发动机， 并 且还用于当所述第一闭式泵或第二闭式泵出现故障时， 相应地停止所述第一 发动机或第二发动机。 进一步地， 所述控制器还用于检测所述第一发动机和第二发动机的转速 并计算二者的差值； 在所述差值大于预设值的情况下， 若当前作业为上升作 业， 则提高转速较低的发动机的转速； 若当前作业为下降作业， 则减小转速 较高的发动机对应的泵的排量。 进一步地， 所述控制器与所述第一闭式泵、 第二闭式泵以及所述液压马 达连接， 用于检测液压马达的转速； 调节所述第一闭式泵和第二闭式泵的排 量， 使液压马达的转速为预设值。 为了实现上述目的，才艮据本发明的另一方面，提供了一种液压控制方法。 本发明的这种液压控制方法应用于本发明的液压控制系统，该方法包括： 当所述第一闭式泵或第二闭式泵出现故障时， 相应地停止所述第一发动机或 第二发动机。 为了实现上述目的， 才艮据本发明的另一方面， 提供了又一种液压控制方 法。 本发明的这种液压控制方法应用于本发明的液压控制系统，该方法包括： 检测所述液压控制系统中的第一发动机和第二发动机的转速并计算二者的差 值； 在所述差值大于预设值的情况下， 若当前作业为上升作业， 则提高转速 较低的发动机的转速； 若当前作业为下降作业， 则减小转速较高的发动机对 应的泵的排量。 进一步地， 该方法还包括： 检测液压马达的转速； 调节所述第一闭式泵 和第二闭式泵的排量， 使液压马达的转速为预设值。 为了实现上述目的， 才艮据本发明的另一方面， 提供了又一种液压控制方 法。 本发明的这种液压控制方法应用于本发明的液压控制系统，该方法包括： 检测液压马达的转速； 调节所述第一闭式泵和第二闭式泵的 4 量， 使液压马 达的转速为预设值。 应用本发明的技术方案， 通过釆用并联的泵， 从而可以选用较小功率的 发动机， 使得发动机的选型范围较大； 本发明釆用闭式泵， 无需节流控制的 相关管路与部件例如换向阀， 因此液压管路简单， 发热量小， 故障源较少； 而且减少了由于阀件的开闭而产生的冲击， 从而提高了动作的啟动性能。 附图说明 构成本说明书的一部分、 用于进一步理解本发明的附图示出了本发明的 优选实施例， 并与说明书一起用来说明本发明的原理。 图中： 图 1是 居本发明实施例中的液压控制系统结构的示意图。 具体实施方式 需要说明的是， 在不冲突的情况下， 本申请中的实施例及实施例中的特 征可以相互组合。 下面将参考附图并结合实施例来详细说明本发明。 图 1是 居本发明实施例中的液压控制系统结构的示意图。 如图 1所示， 本发明实施例中的液压控制系统主要包括第一发动机 Ml 和与之连接的第一闭式泵 Pl、 第二发动机 M2和与之连接的第二闭式泵 P2、 液压马达 P3。 液压马达 P3作为执行元件。 其中第一闭式泵 Pl、 第二闭式泵 P2和液压马达 P3并联， 即第一闭式 泵 P1的高压口 Al、 第二闭式泵 P2的高压口 A2、 液压马达 P3的 A口互相 连接； 即第一闭式泵 P1的氐压口 Bl、 第二闭式泵 P2的氐压口 B2、 液压马 达 P3的 B口互 目连接。 本实施例中的液压控制系统还可以包括制动器 12 , 以实现对负载 13运 动的制动。 另外本实施例中的液压控制系统还可以包括控制器 11 , 该控制器 11可以釆用现有的控制器件， 例如可编程逻辑控制器 PLC。 控制器 11与第一发动机 Ml和第二发动机 M2连接，用以对这两个发动 机的转速进行控制， 从而实现对这两个发动机的输出扭矩的控制， 并可以实 现对这两个发动机的启动和停止的控制。 以下对本实施例中的液压控制方法作出说明。 该液压控制方法可以釆用 现有的控制器件例如 PLC来实现。 为了控制第一发动机 Ml和第二发动机 M2的扭矩， 以避免因扭矩不足 而熄火或者扭矩过大而飞车， 控制器可以检测第一发动机 Ml和第二发动机 M2的转速并且计算二者的差值， 若该差值大于预设的范围， 那么： 如果当 前作业为上升作业， 则提高转速较氏的发动机的转速， 如果当前作业为下降 作业， 则减小转速较高的发动机对应的泵的排量， 从而将闭式泵的输出功率 控制在允许范围内， 例如第二发动机 M2的转速较高， 则减小第二闭式泵 P2 的排量。 有关差值的预设范围可以通过试-险加以确定。 这里的上升作业和下 降作业分别指起重机将负载从低处提升至高处， 和将负载从高处放至低处。 如果需要调节负载的上升或下降的速度， 控制器 11可以检测液压马达 P3的转速， 并且调节第一闭式泵 P1和第二闭式泵 P2的排量， 使液压马达 P3的转速为预设值。 在本实施例中， 可以由起重机的操作人员观察负载运动速度然后通过对 操纵手柄 10的操作来实现液压马达的转速为预设值， 此时负载的运动速度 也符合作业要求。 如果第一闭式泵 P1或第二闭式泵 P2出现故障， 则由控制器 11相应地 停止第一发动机 Ml或第二发动机 M2, 此时相应地只由第二发动机 M2或 第一发动机 Ml工作。 这样， 第一发动机 Ml和第二发动机 M2之间形成互 为备用的关系， 从而提高了系统的可靠性。 从以上的描述中， 可以看出， 应用本实施例的技术方案， 通过釆用并联 的泵， 从而可以选用较小功率的发动机， 使得发动机的选型范围较大； 而本 发明实施例中釆用闭式泵， 无需节流控制的相关管路与部件例如换向阀， 因 此液压管路简单， 发热量小， 故障源较少； 而且减少了由于阀件的开闭而产 生的冲击， 从而提高了动作的微动性能。 以上所述仅为本发明的优选实施例而已， 并不用于限制本发明， 对于本 领域的技术人员来说， 本发明可以有各种更改和变化。 凡在本发明的^"神和 原则之内， 所作的任何修改、 等同替换、 改进等， 均应包含在本发明的保护 范围之内。

Claims

权 利 要 求 书 一种液压控制系统， 其特征在于， 包括：
相互连接的第一闭式泵和第一发动机；
相互连接的第二闭式泵和第二发动机；
液压马达； 其中，
所述第一闭式泵、 第二闭式泵和所述液压马达并联。 根据权利要求 1所述的液压控制系统， 其特征在于， 还包括制动器， 连接在所述液压马达的输出端。 才艮据权利要求 1或 2所述的液压控制系统， 其特征在于， 还包括与所 述第一发动机和所述第二发动机连接的控制器， 该控制器用于启动所 述第一发动机和第二发动机， 并且还用于当所述第一闭式泵或第二闭 式泵出现故障时， 相应地停止所述第一发动机或第二发动机。 根据权利要求 3所述的液压控制系统， 其特征在于， 所述控制器还用 于检测所述第一发动机和第二发动机的转速并计算二者的差值；
在所述差值大于预设值的情况下，
若当前作业为上升作业， 则提高转速较低的发动机的转速； 若当前作业为下降作业，则减 , j、转速较高的发动机对应泵的排量。 根据权利要求 4所述的液压控制系统， 其特征在于， 所述控制器进一 步与所述第一闭式泵、 第二闭式泵以及所述液压马达连接， 用于： 检测液压马达的转速；
调节所述第一闭式泵和第二闭式泵的排量， 使液压马达的转速为 预设值。 才艮据权利要求 1或 2所述的液压控制系统， 其特征在于， 还包括与所 述第一闭式泵、 第二闭式泵以及所述液压马达连接的控制器， 用于： 检测液压马达的转速； 调节所述第一闭式泵和第二闭式泵的排量， 使液压马达的转速为 预设值。
7. —种液压控制方法， 应用于权利要求 1所述的液压系统， 其特征在于， 该方法包括： 当所述第一闭式泵或第二闭式泵出现故障时， 相应地停 止所述第一发动机或第二发动机。
8. —种液压控制方法， 应用于权利要求 1所述的液压系统， 其特征在于， 该方法包括：
检测所述液压控制系统中的第一发动机和第二发动机的转速并计 算二者的差值；
在所述差值大于预设值的情况下，
若当前作业为上升作业， 则提高转速较低的发动机的转速； 若当前作业为下降作业， 则减 , j、转速较高的发动机对应的泵的排 量。
9. 根据权利要求 8所述的方法， 其特征在于， 还包括：
检测液压马达的转速；
调节所述第一闭式泵和第二闭式泵的排量， 使液压马达的转速为 预设值。
10. —种液压控制方法， 应用于权利要求 1所述的液压系统， 其特征在于， 该方法包括：
检测液压马达的转速；
调节所述第一闭式泵和第二闭式泵的排量， 使液压马达的转速为 预设值。
PCT/CN2011/072627 2010-04-13 2011-04-11 液压控制系统和液压控制方法 Ceased WO2011127807A1 (zh)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US13/641,096 US20130091833A1 (en) 2010-04-13 2011-04-11 Hydraulic control system and hydraulic control method

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201010145313.8A CN101922485B (zh) 2010-04-13 2010-04-13 液压控制系统和液压控制方法
CN201010145313.8 2010-04-13

Publications (1)

Publication Number Publication Date
WO2011127807A1 true WO2011127807A1 (zh) 2011-10-20

Family

ID=43337611

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2011/072627 Ceased WO2011127807A1 (zh) 2010-04-13 2011-04-11 液压控制系统和液压控制方法

Country Status (3)

Country Link
US (1) US20130091833A1 (zh)
CN (1) CN101922485B (zh)
WO (1) WO2011127807A1 (zh)

Families Citing this family (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101922485B (zh) * 2010-04-13 2014-02-19 中联重科股份有限公司 液压控制系统和液压控制方法
CN102275493A (zh) * 2011-06-09 2011-12-14 上海三一科技有限公司 具有双发动机的动力系统及包括该动力系统的起重机
CN103486098B (zh) * 2012-06-13 2016-04-13 徐工集团工程机械股份有限公司 闭式液压系统以及起重机
DE102013103722B4 (de) * 2013-04-12 2016-10-13 Thyssenkrupp Tiefbautechnik Gmbh Vibrationsrammanordnung sowie Verfahren zum Betrieb der Vibrationsrammanordnung
SG11201607066SA (en) 2014-02-28 2016-09-29 Project Phoenix Llc Pump integrated with two independently driven prime movers
US10465721B2 (en) 2014-03-25 2019-11-05 Project Phoenix, LLC System to pump fluid and control thereof
WO2015164453A2 (en) 2014-04-22 2015-10-29 Afshari Thomas Fluid delivery system with a shaft having a through-passage
WO2015187673A1 (en) 2014-06-02 2015-12-10 Afshari Thomas Linear actuator assembly and system
WO2015187681A1 (en) 2014-06-02 2015-12-10 Afshari Thomas Hydrostatic transmission assembly and system
AU2015292611B2 (en) 2014-07-22 2019-07-04 Project Phoenix, LLC External gear pump integrated with two independently driven prime movers
US10072676B2 (en) 2014-09-23 2018-09-11 Project Phoenix, LLC System to pump fluid and control thereof
EP3204647B1 (en) * 2014-10-06 2021-05-26 Project Phoenix LLC Linear actuator assembly and system
US10677352B2 (en) 2014-10-20 2020-06-09 Project Phoenix, LLC Hydrostatic transmission assembly and system
CN104442373A (zh) * 2014-12-01 2015-03-25 岑溪市东正动力科技开发有限公司 汽车可变排量驱动系统
US11085440B2 (en) 2015-09-02 2021-08-10 Project Phoenix, LLC System to pump fluid and control thereof
TWI768455B (zh) 2015-09-02 2022-06-21 美商鳳凰計劃股份有限公司 泵送流體之系統及其控制
EP4145686B1 (en) 2016-08-17 2025-07-16 Project Phoenix, LLC Fluid system with motor operated accumulator
CA3110135C (en) * 2018-08-21 2023-09-05 Siemens Energy, Inc. Double-acting hydraulic actuator with different pumps for each actuation direction
EP4179211A1 (en) 2020-07-08 2023-05-17 Project Phoenix, LLC Dynamic control of gears in a gear pump having a drive-drive configuration
US12535071B2 (en) 2020-07-08 2026-01-27 Project Phoenix, LLC Dynamic control of gears in a gear pump having a drive-drive configuration
CN116658493B (zh) * 2023-08-01 2023-10-24 华侨大学 基于变转速与变排量的负流量系统和电动工程机械装置

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5428970A (en) * 1977-08-04 1979-03-03 Japan Steel Works Ltd:The Hydraulic circuit
JP2003294008A (ja) * 2002-04-04 2003-10-15 Kayaba Ind Co Ltd 油圧制御装置
JP2003301802A (ja) * 2002-02-06 2003-10-24 Kayaba Ind Co Ltd ミキサ車
CN2931433Y (zh) * 2006-06-12 2007-08-08 上海三一科技有限公司 闭式升降液压系统
CN100462571C (zh) * 2005-01-18 2009-02-18 上海市离心机械研究所有限公司 一种用于卧螺离心机成套系统的双泵驱动液压站
CN101709725A (zh) * 2009-11-17 2010-05-19 华东交通大学 一种采用多泵组合技术的井下防爆提升机液压控制系统
CN201526546U (zh) * 2009-11-17 2010-07-14 华东交通大学 一种采用多泵组合技术的井下防爆提升机液压控制系统
CN101922485A (zh) * 2010-04-13 2010-12-22 长沙中联重工科技发展股份有限公司 液压控制系统和液压控制方法

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0779239B2 (de) * 1995-12-13 2006-09-13 Liebherr-Werk Ehingen GmbH Steuervorrichtung für ein Hubwerk eines Krans
JP3884178B2 (ja) * 1998-11-27 2007-02-21 日立建機株式会社 旋回制御装置
CN2668907Y (zh) * 2003-12-05 2005-01-05 江苏省机电研究所有限公司 伸缩臂式高空作业车幅度控制系统
CN2717915Y (zh) * 2004-04-30 2005-08-17 长沙中联重工科技发展股份有限公司浦沅分公司 一种起重机用闭式回转驱动液压机构
DE102006040459B4 (de) * 2005-09-07 2012-12-13 Terex Demag Gmbh Hydrauliksteuerkreis
US7549287B2 (en) * 2007-09-14 2009-06-23 Cnh America Llc Hydrostatic auto/manual speed control
CN201246355Y (zh) * 2008-05-24 2009-05-27 邱景发 起重机液压变速装置

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5428970A (en) * 1977-08-04 1979-03-03 Japan Steel Works Ltd:The Hydraulic circuit
JP2003301802A (ja) * 2002-02-06 2003-10-24 Kayaba Ind Co Ltd ミキサ車
JP2003294008A (ja) * 2002-04-04 2003-10-15 Kayaba Ind Co Ltd 油圧制御装置
CN100462571C (zh) * 2005-01-18 2009-02-18 上海市离心机械研究所有限公司 一种用于卧螺离心机成套系统的双泵驱动液压站
CN2931433Y (zh) * 2006-06-12 2007-08-08 上海三一科技有限公司 闭式升降液压系统
CN101709725A (zh) * 2009-11-17 2010-05-19 华东交通大学 一种采用多泵组合技术的井下防爆提升机液压控制系统
CN201526546U (zh) * 2009-11-17 2010-07-14 华东交通大学 一种采用多泵组合技术的井下防爆提升机液压控制系统
CN101922485A (zh) * 2010-04-13 2010-12-22 长沙中联重工科技发展股份有限公司 液压控制系统和液压控制方法

Also Published As

Publication number Publication date
CN101922485A (zh) 2010-12-22
US20130091833A1 (en) 2013-04-18
CN101922485B (zh) 2014-02-19

Similar Documents

Publication Publication Date Title
WO2011127807A1 (zh) 液压控制系统和液压控制方法
CN102912823B (zh) 一种挖掘机回转节能系统
CN101799022B (zh) 多泵工作控制方法、控制器、控制系统及起重机
CN102588358B (zh) 一种高性能节能型的电液伺服控制油路
KR102156446B1 (ko) 건설기계의 유압시스템
CN102079482B (zh) 起重机及其复合动作的控制方法、控制器
CN103010980B (zh) 回转控制液压系统及起重机
CN103727076B (zh) 一种液控回转控制装置及起重机回转系统
CN102229328A (zh) 一种多泵合流的车辆机械节能液压系统
WO2012174937A1 (zh) 一种搭载负载敏感主阀与正流量泵的挖掘机液压系统
CN103334979B (zh) 双液压缸同步控制系统及应用该控制系统的工程机械
CN201801313U (zh) 起重机及其复合动作的控制器
CN103644159A (zh) 遥控盒控制阀及转台液压控制系统、起重机
CN103641023B (zh) 控制阀及卷扬制动器的液压控制系统、起重机
CN208185091U (zh) 正控制负载敏感系统
US20120233995A1 (en) Hybrid operating machine
CN103132557B (zh) 挖掘机及其优先控制回路
CN104176639B (zh) 变恒压网络液压系统、液压控制方法及起重机
CN105102732B (zh) 建筑机械的阀芯位移可变控制装置及控制方法
CN112938720A (zh) 自适应调速的驱动力、制动力闭环调整的双功能液压系统
CN104912136B (zh) 一种挖掘机及其回转液压系统
CN103195764A (zh) 两级双向高精度液压同步控制系统
CN204111197U (zh) 变恒压网络液压系统及起重机
CN103727078B (zh) 起重机及其液压系统
CN103216477A (zh) 一种单动力液压源的定量泵压力补偿方法及装置

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 11768419

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

WWE Wipo information: entry into national phase

Ref document number: 9023/CHENP/2012

Country of ref document: IN

WWE Wipo information: entry into national phase

Ref document number: 13641096

Country of ref document: US

122 Ep: pct application non-entry in european phase

Ref document number: 11768419

Country of ref document: EP

Kind code of ref document: A1