WO2023036000A1 - 一种闭式液压控制系统及工程机械 - Google Patents

一种闭式液压控制系统及工程机械 Download PDF

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Publication number
WO2023036000A1
WO2023036000A1 PCT/CN2022/115413 CN2022115413W WO2023036000A1 WO 2023036000 A1 WO2023036000 A1 WO 2023036000A1 CN 2022115413 W CN2022115413 W CN 2022115413W WO 2023036000 A1 WO2023036000 A1 WO 2023036000A1
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Prior art keywords
oil
valve
closed
hydraulic control
pressure side
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PCT/CN2022/115413
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English (en)
French (fr)
Inventor
孔令奇
任行
许显华
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三一石油智能装备有限公司
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Publication of WO2023036000A1 publication Critical patent/WO2023036000A1/zh

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    • 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C13/00—Other constructional features or details
    • B66C13/18—Control systems or devices
    • B66C13/20—Control systems or devices for non-electric drives
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • 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
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/88—Control measures for saving energy

Definitions

  • the invention relates to the technical field of hydraulic control, in particular to a closed hydraulic control system and engineering machinery.
  • the closed hydraulic system has the advantages of stable reversing, small impact and high efficiency, and is widely used in construction machinery.
  • some construction machinery such as hydraulic jib tower cranes and crawler cranes, there are often multiple actuators such as luffing, lifting, and slewing, and these actuators are generally controlled by closed hydraulic subsystems.
  • the hydraulic oil flows from the variable pump to the actuator and then back to the variable pump, and circulates inside the system without returning to the oil tank.
  • the total amount of oil remains unchanged, but in actual work, it cannot Avoid leakage and loss (continuous internal leakage of high-pressure oil is an inherent product of component design), so a charge circuit is often set up, and the leaked and lost hydraulic oil is replenished in time through the charge pump.
  • the charge pump needs to supply oil to the closed hydraulic system at all times.
  • the charge pump does nothing else. All hydraulic oil overflows from the charge relief valve of the charge pump, and this part of power loss is converted into heat, resulting in a large amount of energy loss.
  • the invention aims at reducing the energy loss when the charge pump supplies oil to the closed system.
  • the present invention provides a closed hydraulic control system, comprising:
  • an oil replenishment system connected to the closed main system and configured to replenish the closed main system
  • An oil unloading system is connected with the closed main system through the control valve group, and the control valve group is suitable for connecting or disconnecting the closed main system with the oil unloading system.
  • a closed hydraulic control system provided by the present invention has, but is not limited to, the following beneficial effects:
  • the closed main system no matter whether the closed main system is in the standby state or in the working state, the closed main system will have leakage and loss, so the oil replenishment system replenishes oil to the closed main system at all times. And in order to ensure that the supplementary flow of the oil supplement system to the closed main system can offset the leakage flow of the closed main system, it is necessary to make the supplementary flow of the oil supplement system to the closed main system greater than the leakage flow in the closed main system. Then there is a part of excess flow. When the closed main system is working, the excess flow can be overflowed back to the oil tank by the supplementary oil system.
  • the control valve group can connect the closed main system The oil system is connected, and then the excess flow is unloaded to the oil tank by the oil unloading system.
  • the centrally closed main system of the present invention when the centrally closed main system of the present invention is in standby, it does not need to be overflowed and lowered by the oil replenishment system itself, which reduces the oil replenishment back pressure (generated during overflow) back pressure), realizing energy saving.
  • the end of the oil unloading system away from the control valve group is connected to the oil tank through a filter.
  • the closed main system includes a closed circuit, a main oil pump and an actuator, the closed circuit includes a high-pressure side circuit and a low-pressure side circuit, and the main oil pump passes through the high-pressure side circuit and the low-pressure side circuit respectively.
  • the circuit is connected with the actuator, and the main oil pump is suitable for driving connection with the actuator.
  • the oil replenishment system includes an oil replenishment circuit, an oil replenishment pump and an oil replenishment overflow valve arranged on the oil replenishment circuit, the oil replenishment circuit is connected with a closed circuit, and the oil replenishment overflow valve is located at Between the charge pump and the closed circuit.
  • the main oil pump is a two-way variable pump
  • the actuator is a hydraulic motor
  • the closed hydraulic control system also includes a shunt pipe, the oil supply system is respectively connected to the high-pressure side circuit and the low-pressure side circuit through the two shunt pipes, and the shunt pipe is provided with a one-way valve, and the one-way valve restricts the flow of oil from the supplementary oil system to the high-pressure side circuit and the low-pressure side circuit.
  • the oil unloading system includes an oil unloading circuit and an electromagnetic unloading valve arranged on the oil unloading circuit, the oil unloading circuit is connected to the closed circuit through the control valve group, and the high pressure side
  • the high-pressure oil in the circuit flows into the oil outlet of the electromagnetic unloading valve through the control valve group
  • the low-pressure oil in the low-pressure side circuit flows into the control oil port of the electromagnetic unloading valve through the control valve group.
  • control valve group includes a shuttle valve and a hydraulic control reversing valve
  • the electromagnetic unloading valve includes an electromagnetic reversing valve and a hydraulic control check valve
  • the high-pressure oil in the high-pressure side circuit passes through the shuttle valve
  • the low-pressure oil in the low-pressure side circuit flows into the oil inlet of the electromagnetic directional valve through the hydraulic control directional valve, and the first oil of the electromagnetic directional valve
  • An oil outlet is connected to the piston ejector rod of the hydraulic control check valve.
  • the oil outlet of the hydraulic control check valve is the oil outlet of the electromagnetic unloading valve
  • the oil inlet of the hydraulic control check valve is the oil inlet of the electromagnetic unloading valve
  • the oil inlet port of the electromagnetic reversing valve is the control oil port of the electromagnetic unloading valve.
  • first oil inlet of the shuttle valve communicates with the high-pressure side circuit
  • second oil inlet of the shuttle valve communicates with the low-pressure side circuit
  • the oil outlet of the shuttle valve communicates with the high-pressure side circuit.
  • the oil outlet of the hydraulic control check valve is connected.
  • the present invention also provides a construction machine, including the aforementioned closed hydraulic control system.
  • Fig. 1 is a schematic diagram of a closed hydraulic control system according to an embodiment of the present invention.
  • 1-Closed main system 11-Closed circuit, 111-High pressure side circuit, 112-Low pressure side circuit, 12-Main oil pump, 13-Actuator, 2-Supplement oil system, 21-Supplement oil circuit, 22-Supplement Oil pump, 23-refill oil relief valve, 3-oil unloading system, 31-oil unloading circuit, 32-electromagnetic unloading valve, 321-hydraulic control check valve, 322-electromagnetic reversing valve, 4-filter, 5 - shunt pipe, 51 - one-way valve, 6 - control valve group, 61 - shuttle valve, 62 - hydraulic control reversing valve.
  • the Z axis in the accompanying drawings represents the vertical direction, that is, the up and down position, and the positive direction of the Z axis (that is, the arrow pointing to the Z axis) represents the upper direction, and the negative direction of the Z axis (that is, the opposite direction to the positive direction of the Z axis) Direction) means down;
  • the Y axis in the attached figure means the horizontal direction, that is, the left and right position, and the positive direction of the Y axis (that is, the arrow pointing to the Y axis) represents the left, and the negative direction of the Y axis (that is, the positive direction with the Y axis Opposite direction) means right.
  • a closed hydraulic control system includes a closed main system 1 , an oil replenishment system 2 and an oil unloading system 3 .
  • the oil replenishment system 2 is connected to the closed main system 1 and is used to replenish oil to the closed main system 1, and the oil unloading system 3 is connected to the closed main system 1 through the control valve group 6
  • the control valve group 6 is suitable for connecting or disconnecting the closed main system 1 with the oil unloading system 3 .
  • the closed main system 1 regardless of whether the closed main system 1 is in the standby state or in the working state, the closed main system 1 will have leakage and loss, so the oil replenishment system 2 replenishes the closed main system 1 at all times. of. And in order to ensure that the supplementary flow of the oil supply system 2 to the closed main system 1 can offset the leakage flow of the closed main system 1, it is necessary to make the supplementary flow of the oil supply system 2 to the closed main system 1 greater than that of the closed main system 1, and then a part of the excess flow remains, for example, when the closed main system is working, the excess flow can be overflowed back to the oil tank by the supplementary oil system 2, and when the closed main system 1 is on standby, the control valve Group 6 can communicate the closed main system 1 with the oil unloading system 3, and then the oil unloading system 3 unloads this part of excess flow.
  • the oil replenishment system 2 does not need to overflow and reduce the pressure by itself, which reduces the oil replenishment back pressure ( The back pressure generated during the overflow, the back pressure leads to energy loss), and energy saving is realized.
  • the end of the oil unloading system 3 away from the control valve group 6 is connected to the oil tank through a filter 4 .
  • the closed main system 1 when the closed main system 1 is on standby, the oil in the closed main system 1 is unloaded and the hydraulic oil is filtered through the filter 4 to filter out impurities in the pipeline. That is, when the closed main system 1 is on standby, it functions as a filter, improves the cleanliness of the hydraulic oil, and improves the service life of the equipment.
  • a filter can also be arranged at the initial end of the oil supply system 2 .
  • the closed main system 1 includes a closed circuit 11 , a main oil pump 12 and an actuator 13 .
  • the closed circuit includes a high-pressure side circuit 111 and a low-pressure side circuit 112.
  • the main oil pump 12 is connected to the actuator 13 through the high-pressure side circuit 111 and the low-pressure side circuit 112 respectively.
  • the main oil pump 12 is suitable for It is drivingly connected with the actuator 13.
  • the closed main system 1 has at least one closed circuit 11 and one main oil pump 12 and one actuator 13 arranged on the closed circuit 11 .
  • the input end of the main oil pump 12 is connected to the output end of the actuator 13 , and the output end of the main oil pump 12 is connected to the input end of the actuator 13 , thus forming a closed main system 1 .
  • the oil replenishment system 2 includes an oil replenishment circuit 21, an oil replenishment pump 22 and an oil replenishment overflow valve 23 arranged on the oil replenishment circuit 21, and the oil replenishment circuit 21 is connected to a closed The circuit 11 is connected, and the charge oil relief valve 23 is located between the charge oil pump 22 and the closed circuit 11 .
  • the oil unloading system 3 includes an oil unloading circuit 31 and an electromagnetic unloading valve 32 arranged on the oil unloading circuit 31 , and the oil unloading circuit 31 communicates with the control valve group 6 The closed loop 11 is connected.
  • the main oil pump 12 is a two-way variable pump
  • the actuator 13 is a hydraulic motor.
  • the actuator 13 in the closed main system 1 adopts a double-acting single-piston rod hydraulic cylinder, the power utilization rate will decrease during the working process due to the unequal flow rate of the large and small chambers. Therefore, in this embodiment, the actuator 13 in the closed main system 1 is selected as a hydraulic motor.
  • variable pump is easy to operate, and can reduce the displacement according to the working conditions, thereby reducing the power consumption of the engine and reducing heat generation.
  • the advantage of the quantitative motor is that it is cheap, because the motor has a wide working range and can adapt to flow changes. In this way, the system The layout is simple.
  • the displacement of the main oil pump can be directly changed to gradually approach the required speed.
  • the starting torque of the main oil pump 12 is proportional to the displacement when the pressure is constant, and general prime movers (engines, motors, etc.) are required to start at a small torque, which requires the pump to be variable. of. Therefore, the main oil pump here is a variable pump.
  • the main oil pump 12 is preferably a two-way variable pump, which not only has the function of adjusting the flow rate, but also has the dual function of changing the flow direction, and can continuously adjust the speed and rotation direction of the hydraulic motor without setting a reversing valve in the main oil circuit. Oil flow loss is small.
  • the closed main system 1 is on standby, which means that the main oil pump 12 is idle and on standby without displacement, that is to say, the main oil pump 12 does not supply oil to the motor.
  • the idle main oil pump 12 and the motor need oil lubrication. Since the main oil pump 12 has no displacement, the pipeline pressure on both sides of the main oil pump 12 will gradually balance. In these oils added, part enters the main oil pump 12 and the motor for lubrication, and leaks into the oil tank, and another part of excess flow enters the oil unloading system 3 for unloading. So that when the closed main system 1 is on standby, the oil replenished by the supplementary oil system 2 will not pass through the supplementary oil relief valve 23 .
  • the closed hydraulic control system further includes a shunt pipe 5, and the oil supply system 2 is respectively connected to the high-pressure side circuit 111 and the low-pressure side circuit 112 through the two shunt pipes 5, And the distribution pipe 5 is provided with a one-way valve 51, the one-way valve 51 restricts the flow of oil from the oil supplement system 2 to the high-pressure side circuit 111 and the low-pressure side circuit 112;
  • control valve group 6 When the closed main system 1 is on standby, the control valve group 6 is suitable for unloading the high-pressure oil in the high-pressure side circuit 111 through the electromagnetic unloading valve 32 .
  • the high-pressure side circuit 111 refers to at least the pipeline between the output end of the main oil pump 12 and the input end of the motor
  • the low-pressure side circuit 112 refers to at least the pipeline between the input end of the main oil pump 12 and the motor. piping between outputs.
  • the pipeline on the upper side is the high-pressure side circuit 111
  • the pipeline on the lower side is the low-pressure side circuit 112.
  • the oil port is the oil discharge port and the lower oil port is the oil inlet
  • the main oil pump 12 drives the motor on the right to rotate clockwise.
  • the upper pipeline is the high-pressure side circuit 111
  • the lower pipeline is the low-pressure side circuit.
  • the pipeline is the low-pressure side circuit 112 .
  • one end of the closed circuit 11 is respectively connected to the low-pressure side circuit 112 and the high-pressure side circuit 111 through two shunt pipes 5, and the upper side pipeline is the high-pressure side circuit 111, and the lower side pipeline is the low-pressure side circuit 112 as an example.
  • the closed main system 1 due to the high oil pressure in the high-pressure side circuit 111, the added oil in the supplementary oil circuit 21 enters the lower low-pressure side circuit 112 from the lower check valve 51 Oil replenishment is carried out, and excess flow overflows back to the fuel tank from the oil replenishment overflow valve 23.
  • the main oil pump 12 When the closed main system 1 is on standby, the main oil pump 12 does not discharge in the upper high-pressure side circuit 111, the oil pressure in the high-pressure side circuit 111 and the oil pressure in the low-pressure side circuit will gradually tend to balance, and the oil supply circuit 21 Most of the replenished oil enters the high-pressure side circuit 111 , and part of the flow enters the main oil pump 12 and the motor for lubrication, and the other part of excess flow is unloaded through the electromagnetic unloading valve 32 under the control of the control valve group 6 . Guarantee energy saving when the closed main system 1 is in standby.
  • the control valve group 6 includes a shuttle valve 61 and a hydraulic control reversing valve 62
  • the electromagnetic unloading valve 32 includes an electromagnetic reversing valve 322 and a hydraulic control check valve 321.
  • the high pressure The high-pressure oil in the side circuit 111 flows into the oil outlet of the hydraulic control check valve 321 through the shuttle valve 61
  • the low-pressure oil in the low-pressure side circuit 112 flows into the solenoid valve through the hydraulic control reversing valve 62 .
  • the oil inlet of the reversing valve 322, the first oil outlet of the electromagnetic reversing valve 322 is connected with the piston rod of the hydraulic control check valve 321, when the electromagnetic reversing valve 322 is energized, the The oil inlet of the electromagnetic reversing valve 322 communicates with the first oil outlet of the electromagnetic reversing valve 322, wherein the oil outlet of the hydraulic control check valve 321 is the oil outlet of the electromagnetic unloading valve 32.
  • the oil inlet of the hydraulic control check valve 321 is the oil inlet of the electromagnetic unloading valve 32
  • the oil inlet of the electromagnetic reversing valve 322 is the control oil port of the electromagnetic unloading valve 32 .
  • the hydraulic control reversing valve 62 connects the low-pressure side circuit 112 with the oil inlet of the electromagnetic reversing valve 322, and the low-pressure oil in the low-pressure side circuit 112 enters the oil inlet of the electromagnetic reversing valve 322 as pilot control oil.
  • the left position of the electromagnetic reversing valve 322 moves to the right, and the low-pressure oil used as the pilot control oil flows out from the first oil outlet of the electromagnetic reversing valve and acts on the hydraulic control check valve 321
  • the piston rod of the piston moves, and then the oil outlet (B port) of the hydraulic control check valve 321 is controlled to communicate with the oil inlet (A port) of the hydraulic control check valve, and the high-pressure oil in the high-pressure side circuit 111 passes through the hydraulic control
  • the one-way valve 321 is unloaded to the oil tank until the oil pressure in the high-pressure side circuit 111 and the oil pressure in the low-pressure side circuit 112 gradually tend to balance.
  • the first oil inlet of the shuttle valve 61 communicates with the high-pressure side circuit 111
  • the second oil inlet of the shuttle valve 61 communicates with the low-pressure side circuit 112
  • the The oil outlet of the shuttle valve 61 communicates with the oil outlet of the hydraulic control check valve 321 .
  • the oil inlet at the left end of the shuttle valve 61 is the first oil inlet
  • the oil inlet at the right end is the second oil inlet
  • the upper end is the oil outlet.
  • the high-pressure oil can communicate with the oil outlet of the hydraulic control check valve 321 through the shuttle valve 61.
  • another embodiment of the present invention also provides a construction machine, including the aforementioned closed hydraulic control system.
  • first and second are used for descriptive purposes only, and cannot be understood as indicating or implying relative importance or implicitly specifying the quantity of indicated technical features. Thus, the features defined as “first” and “second” may explicitly or implicitly include at least one of these features.

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  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Automation & Control Theory (AREA)
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Abstract

公开了一种闭式液压控制系统，包括闭式主系统（1）、补油系统（2）和卸油系统（3）；补油系统（2）与闭式主系统（1）连接且用于对闭式主系统（1）补油，卸油系统（3）通过控制阀组（6）与闭式主系统（1）连接，控制阀组（6）适于将闭式主系统（1）与卸油系统（3）连通或断开，能够实现节能效果；还公开了使用该闭式液压控制系统的工程机械。

Description

一种闭式液压控制系统及工程机械
相关申请的交叉引用
本申请要求于2021年09月08日提交中国专利局，申请号为2021110477708，发明名称为“一种闭式液压控制系统及工程机械”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
本发明涉及液压控制技术领域，具体而言，涉及一种闭式液压控制系统及工程机械。
背景技术
闭式液压系统具有换向平稳，冲击小，效率高等优点，在工程机械中应用非常广泛。在一些工程机械中如液压动臂塔式起重机、履带式起重机等，往往具有多个执行机构如变幅、起升、回转等，这些执行机构一般分别采用闭式液压子系统控制。
在闭式液压系统中，液压油从变量泵流至执行机构再回到变量泵，在系统内部循环而不流回油箱，理论上，油液总量保持不变，但实际工作过程中，不可避免会存在泄漏和损耗(连续的高压油内泄是元件设计的固有产物)，因此往往设置补油回路，通过补油泵及时补充泄漏和损耗的液压油。尤其是当系统待机时，为了保证闭式液压系统内部主油泵和执行机构的润滑，补油泵需要时刻向闭式液压系统中补油，补油泵除了补充闭式液压系统的泄漏和损耗外，其余的液压油均从补油泵的补油溢流阀溢流，这部分功率损失全部转换为热量，造成大量能量损失。
发明内容
本发明旨在减小补油泵对闭式系统补油时的能量损失。
为解决上述问题，本发明提供了一种闭式液压控制系统，包括：
闭式主系统；
补油系统，所述补油系统与所述闭式主系统连接且用于对所述闭式主系统补油；以及
卸油系统，所述卸油系统通过所述控制阀组与所述闭式主系统连接，所述控制阀组适于将所述闭式主系统与所述卸油系统连通或断开。
本发明提供的一种闭式液压控制系统，相较于现有技术，具有但不局限于以下有益效果：
本发明无论闭式主系统是处于待机状态时，还是处于工作状态时，闭式主系统都会有泄漏和损耗，因此补油系统是时刻对闭式主系统进行补油的。且为了保证补油系统对闭式主系统补充的流量能够抵消掉闭式主系统泄漏的流量，需要使补油系统对闭式主系统的补充的流量要大于闭式主系统中泄漏的流量，然后剩余一部分多余的流量，在闭式主系统工作时，多余的流量可由补油系统自行溢流回到油箱，例如，在闭式主系统待机时，控制阀组可将闭式主系统与卸油系统连通，进而由卸油系统将这一部分多余的流量卸荷至油箱。相较于传统的只能由补油系统自身溢流而言，本发明中闭式主系统待机时，不需要由补油系统自行溢流降压，降低了补油背压(溢流时产生的背压)，实现了节能。
进一步地，所述卸油系统远离所述控制阀组的一端通过过滤器与油箱连接。
进一步地，所述闭式主系统包括闭式回路、主油泵和执行机构，所述闭式回路包括高压侧回路和低压侧回路，所述主油泵分别通过所述高压侧回路和所述低压侧回路与所述执行机构连接，所述主油泵适于与所述执行机构驱动连接。
进一步地，所述补油系统包括补油回路、设置于所述补油回路上的补油泵和补油溢流阀，所述补油回路与闭式回路连接，所述补油溢流阀位于所述补油泵与所述闭式回路之间。
进一步地，所述主油泵为双向变量泵，所述执行机构为液压马达。
进一步地，闭式液压控制系统还包括分流管，所述补油系统通过两个所述分流管分别与所述高压侧回路以及所述低压侧回路连接，且所述分流管上设置有单向阀，所述单向阀限定油液从所述补油系统流向所述高压侧回路和所述低压侧回路。
进一步地，所述卸油系统包括卸油回路和设置于所述卸油回路上的电磁卸荷阀，所述卸油回路通过所述控制阀组与所述闭式回路连接，所述高压侧回路中的高压油通过所述控制阀组流入所述电磁卸荷阀的出油口，所述低压侧回路中的低压油通过所述控制阀组流入所述电磁卸荷阀的控制油口。
进一步地，所述控制阀组包括梭阀和液控换向阀，所述电磁卸荷阀包括电磁换向阀和液控单向阀，所述高压侧回路中的高压油通过所述梭阀流入所述液控单向阀的出油口，所述低压侧回路中的低压油通过所述液控换向阀流入所述电磁换向阀的进油口，所述电磁换向阀的第一出油口与所述液控单向阀的活塞顶杆连接，所述电磁换向阀得电时，所述电磁换向阀的进油口与所述电磁换向阀的第一出油口连通，其中，所述液控单向阀的出油口为所述电磁卸荷阀的出油口，所述液控单向阀的进油口为所述电磁卸荷阀的进油口，所述电磁换向阀的进油口为所述电磁卸荷阀的控制油口。
进一步地，所述梭阀的第一进油口与所述高压侧回路连通，所述梭阀的第二进油口与所述低压侧回路连通，所述梭阀的出油口与所述液控单向阀的出油口连通。
另外，本发明还提供一种工程机械，包括如前述的闭式液压控制系统。
由于所述工程机械的技术改进和取得的技术效果与所述闭式液压控制系统一样，因此不再对所述工程机械的技术效果做出详细说明。
附图说明
图1为本发明实施例的闭式液压控制系统的原理图。
附图标记说明：
1-闭式主系统，11-闭式回路，111-高压侧回路，112-低压侧回路，12-主油泵，13-执行机构，2-补油系统，21-补油回路，22-补油泵，23-补油溢流阀，3-卸油系统，31-卸油回路，32-电磁卸荷阀，321-液控单向阀，322-电磁换向阀，4-过滤器，5-分流管，51-单向阀，6-控制阀组，61-梭阀，62-液控换向阀。
具体实施方式
为使本发明的上述目的、特征和优点能够更为明显易懂，下面结合附图对本发明的具体实施例做详细的说明。
在本发明的描述中，需要理解的是，术语“上”、“下”、“左”、“右”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本发明和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本发明的限制。
而且，附图中Z轴表示竖向，也就是上下位置，并且Z轴的正向(也就是Z轴的箭头指向)表示上，Z轴的负向(也就是与Z轴的正向相反的方向)表示下；附图中Y轴表示横向，也就是左右位置，并且Y轴的正向(也就是Y轴的箭头指向)表示左，Y轴的负向(也就是与Y轴的正向相反的方向)表示右。
同时需要说明的是，前述Z、Y轴的表示含义仅是为了便于描述本发明和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本发明的限制。
参见图1，本发明实施例的一种闭式液压控制系统，包括闭式主系统1、补油系统2和卸油系统3。所述补油系统2与所述闭式主系统1连接且用于对所述闭式主系统1补油，所述卸油系统3通过所述控制阀组6与所述闭式主系统1连接，所述控制阀组6适于将所述闭式主系统1与所述卸油系统3连通或断开。
本实施例中，无论闭式主系统1是处于待机状态时，还是处于工作状态时，闭式主系统1都会有泄漏和损耗，因此补油系统2是时刻对闭式主系统1 进行补油的。且为了保证补油系统2对闭式主系统1补充的流量能够抵消掉闭式主系统1泄漏的流量，需要使补油系统2对闭式主系统1的补充的流量要大于闭式主系统1中泄漏的流量，然后剩余一部分多余的流量，例如，在闭式主系统工作时，多余的流量可由补油系统2自行溢流回到油箱，而在闭式主系统1待机时，控制阀组6可将闭式主系统1与卸油系统3连通，进而由卸油系统3将这一部分多余的流量卸荷。相较于传统的只能由补油系统2自身溢流而言，本实施例中闭式主系统1待机时，不需要由补油系统2自行溢流降压，降低了补油背压(溢流时产生的背压，背压导致能量损耗)，实现了节能。
可选地，参见图1，所述卸油系统3远离所述控制阀组6的一端通过过滤器4与油箱连接。
这里，当闭式主系统1待机时，对闭式主系统1中的油液卸荷并通过过滤器4对液压油进行过滤，将管路中的杂质过滤干净。即闭式主系统1待命时，起到过滤的作用，提高液压油清洁度，提升设备使用寿命。
可以理解的是，在补油系统2的初始端也可以设置一个过滤器。
可选地，参见图1，所述闭式主系统1包括闭式回路11、主油泵12和执行机构13。所述闭式回路包括高压侧回路111和低压侧回路112，所述主油泵12分别通过所述高压侧回路111和所述低压侧回路112与所述执行机构13连接，所述主油泵12适于与所述执行机构13驱动连接。
这里，闭式主系统1最少具有一个闭式回路11和设置在该闭式回路11上的一个主油泵12和一个执行机构13。
可以理解的是，主油泵12的输入端与执行机构13的输出端连接，主油泵12的输出端与执行机构13的输入端连接，如此构成闭式主系统1。
可选地，参见图1，所述补油系统2包括补油回路21、设置于所述补油回路21上的补油泵22和补油溢流阀23，所述补油回路21与闭式回路11连接，所述补油溢流阀23位于所述补油泵22与所述闭式回路11之间。
这里，正如前述所言，在闭式主系统1工作时，多余的流量从补油溢流阀23溢流回油箱中。
可选地，参见图1，所述卸油系统3包括卸油回路31和设置于所述卸油回路31上的电磁卸荷阀32，所述卸油回路31通过所述控制阀组6与所述闭式回路11连接。
这里，卸油系统3对闭式主系统1卸荷时，具体是将补油系统2输入闭式主系统1中多余的流量通过电磁卸荷阀32卸除。
进一步地，所述主油泵12为双向变量泵，所述执行机构13为液压马达。
这里，闭式主系统1中的执行机构13若采用双作用单活塞杆液压缸时，由于大小腔流量不等，在工作过程中，会使功率利用率下降。所以本实施例中闭式主系统1中的执行机构13选为液压马达。
其次，变量泵操作方便，可以根据工况减小排量，从而减小发动机功耗，减小发热，定量马达的好处是价格便宜，因为马达的工作范围较宽，可以适应流量变化，这样系统布置简单，马达的转速需要调节时，直接改变主油泵的排量，逐步接近所需要的转速。从另一方面说，主油泵12的启动扭矩在压力一定的情况下与排量成正比，而一般的原动机(发动机、电动机等)都要求在小的扭矩下启动，这就要求泵为变量的。因此这里主油泵为变量泵。
主油泵12优选为双向变量泵，其不仅兼有调节流量的作用，还可以具有改变流向的双重功能，可连续调节液压马达的转速和旋转方向，无需在主油路中设置换向阀，液压油的流动损失小。
需要说明的是，闭式主系统1待机，即指的是主油泵12空转待命，不排量，也就是说主油泵12不向马达供油。空转待机的主油泵12以及马达需要油液润滑，由于主油泵12不排量，进而主油泵12两侧的管路压力会逐渐平衡，此时补油系统2分别向主油泵12两侧的管路补油，补入的这些油中，部分进入主油泵12和马达中进行润滑，并泄漏至油箱中，另一部分多余的流量进入卸油系统3中卸荷。使得闭式主系统1待机时，补油系统2补入的油不会从补油溢流阀23通过。
可以理解的是，当闭式主系统1工作时，由于主油泵12排量工作以通过高压油驱动马达旋转，则补油系统2是向主油泵12输入端和马达排出端之间的管路上补油，多余的流量从补油溢流阀23溢流回油箱。
参见图1，可选地，闭式液压控制系统还包括分流管5，所述补油系统2通过两个所述分流管5分别与所述高压侧回路111以及所述低压侧回路112连接，且所述分流管5上设置有单向阀51，所述单向阀51限定油液从所述补油系统2流向所述高压侧回路111和所述低压侧回路112；
当所述闭式主系统1待机时，所述控制阀组6适于将所述高压侧回路111中的高压油通过所述电磁卸荷阀32卸荷。
需要说明的是，高压侧回路111指的是至少包括主油泵12的输出端与马达的输入端之间的管路，而低压侧回路112指的是至少包括主油泵12的输入端与马达的输出端之间的管路。图1中闭式主系统1中上侧的管路为高压侧回路111、下侧的管路为低压侧回路112仅为一个示例，由于主油泵12为双向变量泵，则当主油泵12上端的油口为排油口、下端的油口为进油口时，主油泵12驱动右侧的马达顺时针旋转，此时，上侧的管路为高压侧回路111，下侧的管路为低压侧回路112；当主油泵12的下端油口为排油口、上端油口为进油口时，则驱动右侧的马达逆时针旋转，此时下侧的管路为高压侧回路111，上侧的管路为低压侧回路112。
这里，闭式回路11的一端通过两个分流管5分别与低压侧回路112、高压侧回路111连接，以上侧的管路为高压侧回路111、下侧的管路为低压侧回路112为例进行说明，闭式主系统1工作时，由于高压侧回路111中的油压高，补油回路21中的补入的油从下侧的单向阀51中进入下侧的低压侧回路112中进行补油，多余的流量从补油溢流阀23溢流回油箱。闭式主系统1待机时，主油泵12不向上侧的高压侧回路111中排量，高压侧回路111中的油压与低压侧回路中的油压会逐渐趋于平衡，补油回路21中补入的油大部分进入高压侧回路111，并且一部分流量进入主油泵12和马达中润滑，另一部分多余的流量在控制阀组6的控制下通过电磁卸荷阀32卸荷。保证闭式主系统1待机时的节能。
可选地，参见图1，所述控制阀组6包括梭阀61和液控换向阀62，所述电磁卸荷阀32包括电磁换向阀322和液控单向阀321，所述高压侧回路111中的高压油通过所述梭阀61流入所述液控单向阀321的出油口，所述低压侧回路112中的低压油通过所述液控换向阀62流入所述电磁换向阀322的进油 口，所述电磁换向阀322的第一出油口与所述液控单向阀321的活塞顶杆连接，所述电磁换向阀322得电时，所述电磁换向阀322的进油口与所述电磁换向阀322的第一出油口连通，其中，所述液控单向阀321的出油口为所述电磁卸荷阀32的出油口，所述液控单向阀321的进油口为所述电磁卸荷阀32的进油口，所述电磁换向阀322的进油口为所述电磁卸荷阀32的控制油口。
这里，闭式主系统1中，上侧的管路为高压侧回路111、下侧的管路为低压侧回路112时，高压侧回路111中油压会驱动液控换向阀62的上位下移，进而液控换向阀62将低压侧回路112与电磁换向阀322的进油口连通，则低压侧回路112中的低压油作为先导控制油进入电磁换向阀322的进油口，通过控制电磁换向阀322得电，进而电磁换向阀322的左位右移，作为先导控制油的低压油从电磁换向阀的第一出油口流出并作用于液控单向阀321的活塞顶杆移动，进而控制液控单向阀321的出油口(B口)与液控单向阀的进油口(A口)连通，则高压侧回路111中的高压油通过液控单向阀321卸荷至油箱，直至高压侧回路111中的油压与低压侧回路112中的油压逐渐趋于平衡。其中，可以理解的是，补入高压侧回路111中的油液中多余的流量随高压油通过液控单向阀卸荷，直至高压侧回路111中的油压与低压侧回路112中的油压平衡。其中，通过图1中液控换向阀的具体结构可知，在油压的作用下，不论主油泵12是正转还是翻转，都是低压侧回路112中的油液作为先导控制油控制液控单向阀321的出油口和进油口连通。
需要说明的是，闭式主系统1待机时，由于低压侧回路112中的低压油作为先导控制油控制液控单向阀321的出油口和进油口连通，但是低压侧回路112中的低压油不会通过液控单向阀321回到油箱，而是高压侧回路111中的高压油通过液控单向阀321卸荷并回到油箱，因此高压侧回路111中的油液相较于低压侧回路112中的油液流失的更多，那么补油时，更多的是向高压侧回路111中补油。
可选地，参见图1，所述梭阀61的第一进油口与所述高压侧回路111连通，所述梭阀61的第二进油口与所述低压侧回路112连通，所述梭阀61的出油口与所述液控单向阀321的出油口连通。
这里，梭阀61左端的进油口为第一进油口，右端的进油口为第二进油口， 上端为出油口，通过梭阀61的设置，始终保证不论主油泵12是否换向，高压油都能通过梭阀61与液控单向阀321的出油口连通。
另外，本发明另一实施例还提供一种工程机械，包括如前述的闭式液压控制系统。
由于所述工程机械的技术改进和取得的技术效果与所述闭式液压控制系统一样，因此不再对所述工程机械的技术效果做出详细说明。
术语“第一”、“第二”仅用于描述目的，而不能理解为指示或暗示相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含地包括至少一个该特征。
虽然本发明公开披露如上，但本发明公开的保护范围并非仅限于此。本领域技术人员在不脱离本发明公开的精神和范围的前提下，可进行各种变更与修改，这些变更与修改均将落入本发明的保护范围。

Claims (10)

  1. 一种闭式液压控制系统，包括：
    闭式主系统(1)；
    补油系统(2)，所述补油系统(2)与所述闭式主系统(1)连接且用于对所述闭式主系统(1)补油；以及
    卸油系统(3)，所述卸油系统(3)通过控制阀组(6)与所述闭式主系统(1)连接，所述控制阀组(6)适于将所述闭式主系统(1)与所述卸油系统(3)连通或断开。
  2. 根据权利要求1所述的闭式液压控制系统，其中，所述卸油系统(3)远离所述控制阀组(6)的一端通过过滤器(4)与油箱连接。
  3. 根据权利要求1所述的闭式液压控制系统，其中，所述闭式主系统(1)包括闭式回路(11)、主油泵(12)和执行机构(13)，所述闭式回路包括高压侧回路(111)和低压侧回路(112)，所述主油泵(12)分别通过所述高压侧回路(111)和所述低压侧回路(112)与所述执行机构(13)连接。
  4. 根据权利要求3所述的闭式液压控制系统，其中，所述补油系统(2)包括补油回路(21)、设置于所述补油回路(21)上的补油泵(22)和补油溢流阀(23)，所述补油回路(21)与所述闭式回路(11)连接，所述补油溢流阀(23)位于所述补油泵(22)与所述闭式回路(11)之间。
  5. 根据权利要求3所述的闭式液压控制系统，其中，所述主油泵(12)为双向变量泵，所述执行机构(13)为液压马达。
  6. 根据权利要求5所述的闭式液压控制系统，其中，还包括分流管(5)，所述补油系统(2)通过两个所述分流管(5)分别与所述高压侧回路(111)以及所述低压侧回路(112)连接，且所述分流管(5)上设置有单向阀(51)，所述单向阀(51)限定油液从所述补油系统(2)流向所述高压侧回路(111)和所述低压侧回路(112)。
  7. 根据权利要求6所述的闭式液压控制系统，其中，所述卸油系统(3)包括卸油回路(31)和设置于所述卸油回路(31)上的电磁卸荷阀(32)，所述卸油回路(31)通过所述控制阀组(6)与所述闭式回路(11)连接，所述 高压侧回路(111)中的高压油通过所述控制阀组(6)流入所述电磁卸荷阀(32)的出油口，所述低压侧回路(112)中的低压油通过所述控制阀组(6)流入所述电磁卸荷阀(32)的控制油口。
  8. 根据权利要求7所述的闭式液压控制系统，其中，所述控制阀组(6)包括梭阀(61)和液控换向阀(62)，所述电磁卸荷阀(32)包括电磁换向阀(322)和液控单向阀(321)，所述高压侧回路(111)中的高压油通过所述梭阀(61)流入所述液控单向阀(321)的出油口，所述低压侧回路(112)中的低压油通过所述液控换向阀(62)流入所述电磁换向阀(322)的进油口，所述电磁换向阀(322)的第一出油口与所述液控单向阀(321)的活塞顶杆连接，当所述电磁换向阀(322)得电时，所述电磁换向阀(322)的进油口与所述电磁换向阀(322)的第一出油口连通，其中，所述液控单向阀(321)的出油口为所述电磁卸荷阀(32)的出油口，所述液控单向阀(321)的进油口为所述电磁卸荷阀(32)的进油口，所述电磁换向阀(322)的进油口为所述电磁卸荷阀(32)的控制油口。
  9. 根据权利要求8所述的闭式液压控制系统，其中，所述梭阀(61)的第一进油口与所述高压侧回路(111)连通，所述梭阀(61)的第二进油口与所述低压侧回路(112)连通，所述梭阀(61)的出油口与所述液控单向阀(321)的出油口连通。
  10. 一种工程机械，包括如权利要求1至9任一所述的闭式液压控制系统。
PCT/CN2022/115413 2021-09-08 2022-08-29 一种闭式液压控制系统及工程机械 WO2023036000A1 (zh)

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