CN114278624B - Closed pump control quick erection system - Google Patents
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Abstract
The invention discloses a closed pump control quick erection system, which uses a servo motor to drive a hydraulic pump, the reversing of a hydraulic cylinder is completed by switching positive and negative inclination angles of a swash plate of the hydraulic pump, and the rotation speed of the servo motor and the displacement of the hydraulic pump jointly determine the output flow so as to control the rising and falling speeds of the hydraulic cylinder; when the load passes through the center of gravity, the servo motor can absorb load potential energy, and when the load descends, the balance valve guides redundant flow into the oil tank, so that the hydraulic pump has proper oil suction and pressure oil flow when the hydraulic cylinder ascends and descends. The gear pump plays a role in supplementing oil in the system; for locking of the load, a switch loop formed by cartridge valves is used for controlling, so that throttling loss caused by locking of the balance valves is avoided, and the load rises and falls and has higher hydraulic efficiency. The closed hydraulic circuit provided by the invention overcomes the defects of the traditional valve-controlled hydraulic system, has the characteristics of higher efficiency, smaller volume and lighter weight, and can realize quick erection of a load.
Description
Technical Field
The invention belongs to the field of hydraulic transmission, and particularly relates to a closed pump control quick erection system.
Background
Along with the great development of the engineering machinery industry in China, the method has important significance in effectively reducing the energy consumption in the loading and erecting work. In the process of erecting a load, hydraulic drive can realize large-scale energy transmission by utilizing hydraulic storage pressure to generate huge thrust, and the hydraulic drive is very suitable for heavy-load operation conditions such as large-scale engineering machinery. In a traditional open valve control vertical loop, the transmission principle is that a hydraulic pump absorbs oil from an oil tank to generate pressure under the drive of a servo motor, hydraulic oil passes through various control valves and finally reaches a hydraulic cylinder to push a load, and finally returns to the oil tank, and the pressure of the system, the speed and the direction of an actuating mechanism are controlled by various hydraulic valves. Guo Shaobo discloses a multi-cylinder collaborative erection hydraulic system, which adopts an open valve to control a double-acting hydraulic cylinder by an erection loop, so that the erection speed and the return-to-flat speed are obviously improved, the emission time is shortened, but the hydraulic system is more complex, thereby leading to larger overall volume of the hydraulic system, and larger throttling loss in the erection and return-to-flat processes. The open valve control quick erection system has obvious defects that firstly, oil is easy to leak, when hydraulic oil passes through various valves, the oil leak is easy to occur due to possible sealing failure at the interface of a pipeline and the valve, and potential safety hazards exist in the load erection process; secondly, the efficiency problem is that in the whole hydraulic system, the loss of a general servo motor and a hydraulic pump accounts for about 10%, the loss of a hydraulic valve accounts for 40% -60%, and only 30% -50% of the hydraulic valve finally reaches an actuating mechanism, so that the efficiency is low; thirdly, the volume problem of the whole hydraulic system is that all elements in the traditional hydraulic system are connected through pipelines, so that the volume of the hydraulic system is increased, the occupied space is occupied, and the load is increased.
Disclosure of Invention
The invention aims to provide a closed pump control quick erection system which can realize quick erection of a load and has the characteristics of higher efficiency, smaller volume and lighter weight compared with the traditional open valve control hydraulic system.
The technical solution for realizing the purpose of the invention is as follows: a closed pump control quick erection system comprises a hydraulic pump, a gear pump, a servo motor, a first hydraulic control reversing valve, a second hydraulic control reversing valve, a first balance valve, a second balance valve, a first two-way cartridge valve, a second two-way cartridge valve, a first electromagnetic reversing valve, a second electromagnetic reversing valve, a first throttling valve, a second throttling valve, a first overflow valve, a second overflow valve and a hydraulic cylinder.
The design of the oil tank mainly considers the difference of the volumes of the positive and negative cavities of the hydraulic cylinder, and plays a role in supplementing oil. The hydraulic pump is a variable pump, the servo motor is directly connected with the hydraulic pump, and the hydraulic pump is used as a power source of a hydraulic system to provide power for the whole system. The gear pump is coaxially connected with the hydraulic pump, and the design of the gear pump and the oil tank mainly considers the positive and negative cavity volume difference of the hydraulic cylinder to play a role in supplementing oil
All the valve elements can be integrated into one hydraulic valve block, and complicated pipeline connection is not needed. The integrated valve block is directly connected with the hydraulic cylinder and the hydraulic pump, and the servo motor provides power, so that the volume of the whole hydraulic system is greatly reduced.
Compared with the prior art, the invention has the remarkable advantages that: the hydraulic pump is driven by a servo motor based on the principle of electric drive liquid transmission, the hydraulic pump drives a hydraulic cylinder through an integrated valve block, the reversing of the hydraulic cylinder is completed by switching the positive and negative inclination angles of a swash plate of the hydraulic pump, the closed loop of the fluid transmission is formed, and the hydraulic pump has the advantages of the traditional hydraulic drive and direct electric drive actuators and only comprises a power supply interface and a mechanical installation interface. The hydraulic self-locking module and the unloading module are used to the greatest extent, so that the safety is improved. The hydraulic system provided can realize that the load is vertical and the erection time is shorter, meanwhile, the stability and reliability in the erection process are ensured, the efficiency of the whole hydraulic system is improved, and the occupied space is smaller.
Drawings
Fig. 1 is a schematic diagram of a closed pump control quick erection hydraulic system of the present invention.
Detailed Description
The invention will be described in further detail with reference to fig. 1 and the specific examples.
Referring to fig. 1, a closed pump control quick erection system comprises a hydraulic pump 1, a gear pump 2, a servo motor 3, a first hydraulic control reversing valve 4.1, a second hydraulic control reversing valve 4.2, a first balance valve 5.1, a second balance valve 5.2, a first two-way cartridge valve 6.1, a second two-way cartridge valve 6.2, a first electromagnetic reversing valve 7.1, a second electromagnetic reversing valve 7.2, a first throttle valve 8.1, a second throttle valve 8.2, a first overflow valve 9.1, a second overflow valve 9.2 and a hydraulic cylinder 10.
The hydraulic pump 1, the gear pump 2 and the servo motor 3 are coaxially and sequentially connected. The hydraulic pump 1 is a variable displacement hydraulic pump, and is provided with a first interface A1 and a second interface A2. The hydraulic cylinder 10 is provided with a third interface A3 and a fourth interface A4, the second interface A2 of the hydraulic pump 1 is respectively communicated with an oil outlet of the gear pump 2 and an interface A of the first hydraulic control reversing valve 4.1 and an oil inlet of the first balance valve 5.1, and an interface A of the first two-way cartridge valve 6.1 through a one-way valve, the interface B of the first two-way cartridge valve 6.1 is respectively communicated with an interface P of the first electromagnetic reversing valve 7.1 and an interface P of the first throttle valve 8.1 through pipelines, the first overflow valve 9.1 is communicated with an oil inlet of the hydraulic cylinder 10, the interface A1 of the hydraulic pump 1 is respectively communicated with an oil outlet of the gear pump 2 and an interface A of the second hydraulic control reversing valve 4.2 through one-way valves, an oil inlet of the second balance valve 5.2 and an interface A of the second balance valve 6.2, an interface B of the second two-way valve 6.2 is respectively communicated with an interface P of the second electromagnetic reversing valve 7.2 through pipelines, an interface B of the second throttle valve 8.2, an interface A of the second throttle valve 9.2, an interface A of the second balance valve 1.2 is communicated with an oil outlet of the second balance valve 2, an oil outlet of the second balance valve 1.2, an oil outlet of the second balance valve 7.2, an interface B of the second balance valve 5.2 is communicated with an interface B of the second electromagnetic valve 1.2 through a valve, an interface B of the second electromagnetic valve 1, an interface B of the interface B1, an interface B of the interface B is communicated with an interface B of the interface C1, and an interface B of the interface C2, and an interface B is communicated with the interface C of the interface C2, and an interface B is communicated with the interface C is communicated with the interface B through the interface B and an interface B, the interface B of the second pilot operated directional valve 4.2 is in communication with the pressure control port of the first balancing valve 5.1.
The closed pump control rapid erection hydraulic system uses a servo motor 3 to drive a hydraulic pump 1, the reversing of a hydraulic cylinder 10 is completed by switching positive and negative inclination angles of a swash plate of the hydraulic pump 1, and the rotation speed of the servo motor 3 and the displacement of the hydraulic pump 1 jointly determine the output flow so as to control the ascending and descending speeds of the hydraulic cylinder 10. The gear pump 2 plays a role in supplementing oil in the system. All valve elements can be integrated into one hydraulic valve block, and complicated pipeline connection is not needed. The integrated valve block is directly connected with the hydraulic cylinder 10 and the hydraulic pump 1, and the servo motor 3 provides power, so that the volume of the whole hydraulic system is greatly reduced. The system design fully considers the area difference of two cavities of the hydraulic cylinder 10, uses a symmetrical oil way to deal with the flow change of oil discharge of the asymmetrical hydraulic cylinder 10, preferentially uses the servo motor 3 to absorb load potential energy when the load is excessively heavy, and uses the balance valve 5.1 to guide redundant flow into an oil tank when the load is reduced, thereby ensuring that the hydraulic pump 1 has proper oil suction and pressure oil flow when the hydraulic cylinder 10 ascends and descends. The gear pump 2 serves to supplement oil in the hydraulic circuit. For locking of the load, a switching loop formed by the first two-way cartridge valve 6.1 and the second two-way cartridge valve 6.2 is used for control, so that throttling loss caused by locking of the load by using a balance valve in a traditional erection system is avoided, and the load is enabled to rise and fall simultaneously with higher hydraulic efficiency.
Referring to fig. 1, the working process of the hydraulic system is described as follows, when the load rises, the hydraulic pump 1 is adjusted to a positive swing angle, the first switch S1 of the first electromagnetic directional valve 7.1 and the second switch S2 of the second electromagnetic directional valve 7.2 are simultaneously powered on, the locking state of the hydraulic cylinder 10 is released, the rotating speed of the servo motor 3 is adjusted, the rodless cavity of the hydraulic cylinder 10 is filled with oil, and the load rises. When the rodless cavity pressure is higher than the set pressure P 1 of the first hydraulic control reversing valve 4.1, the second balance valve 5.2 is opened after the pilot pressure is established, the flow pressure loss after the second balance valve 5.2 is conducted is the preset pressure P 2, at the moment, the rodless cavity side of the hydraulic pump 1 connected with the hydraulic cylinder 10 is in the oil suction and oil supplementing stage through an oil tank, and the pressure loss of P 2 can enable oil to enter an oil inlet of the hydraulic pump 10 without leakage through the second balance valve 5.2. When the load rises to the overweight center position, the hydraulic cylinder 10 generates negative thrust under the action of the load, when the working condition of the traction hydraulic cylinder 10 is loaded, the oil inlet side pressure of the hydraulic pump 1 can rise, the pressure oil side pressure is reduced, when the pressure oil side pressure is reduced below P 1, the second balance valve 5.2 is closed, the oil liquid with a rod cavity of the hydraulic cylinder 10 under the negative thrust is prevented from leaking out through the second balance valve 5.2, the hydraulic cylinder 10 is not controlled, and at the moment, the negative power generated under the negative thrust is absorbed by the servo motor 3. After the load rises to the top end, the first switch S1 and the second switch S2 are powered off, meanwhile, the rotating speed of the servo motor 3 is adjusted to 0rpm, the inclined angle of the inclined plate of the hydraulic pump 1 returns to the zero position, and the hydraulic cylinder 10 is locked by a switch loop formed by the first two-way cartridge valve 6.1 and the second two-way cartridge valve 6.2. When stopping at any position, the same procedure is performed. When the load descends, the hydraulic pump 1 is adjusted to be a negative swing angle, the first switch S1 and the second switch S2 are powered on simultaneously, the locking state of the hydraulic cylinder 10 is released, the rotating speed of the servo motor 3 is adjusted, the hydraulic cylinder 10 is provided with rod cavities for oil feeding, the load descends, and because of the existence of the area difference of the two cavities of the hydraulic cylinder 10, the oil discharge flow of the rodless cavity is larger than the oil feed flow of the rod cavities at the moment, and the hydraulic pump 1 can receive the oil discharge of the rodless cavity without supplementing oil from an oil tank. If the first balance valve 5.1 is not conducted, the redundant flow on the rodless cavity side of the hydraulic cylinder 10 will cause the pressure on the rod cavity side to rise, and when the pressure on the rod cavity side is higher than the set pressure P 3 of the second pilot operated directional valve 4.2, the first balance valve 5.1 is conducted after establishing the pilot pressure, and the redundant flow is leaked from the first balance valve 5.1 to the oil tank. If the hydraulic cylinder 10 is out of control during the load falling process, the pressure of the rod cavity of the hydraulic cylinder 10 tends to drop and even negative pressure occurs, when the pressure of the rod cavity is lower than P 3, the first balance valve 5.1 is closed, and the servo motor 3 is reversely dragged by the hydraulic pump 1 to overspeed to form a braking effect, so that the out-of-control falling of the hydraulic cylinder 10 is prevented. After the load is lowered to the bottom end, the first switch S1 and the second switch S2 are powered off, meanwhile, the rotating speed of the servo motor 3 is adjusted to 0rpm, the swashplate swing angle of the hydraulic pump 1 returns to the zero position, and the hydraulic cylinder 10 is locked by a switch loop formed by the first two-way cartridge valve 6.1 and the second two-way cartridge valve 6.2. When the lowering is stopped at an arbitrary position, the same procedure is performed.
With reference to fig. 1, the system safety is described below, and in the closed loop, sufficient oil supplement and timeliness of oil supplement of the hydraulic pump are preconditions for ensuring safe operation of the hydraulic pump. In the loop, the oil absorption of the hydraulic pump 1 not only receives the return oil of the system, but also can directly absorb the oil from the oil tank, if the oil absorption side has positive pressure, the condition that the hydraulic pump 1 has reliable oil absorption is described, the springless check valve can separate the oil tank and the oil absorption port of the hydraulic pump 1, so that the pressure oil on the oil absorption side is prevented from entering the oil tank, once the negative pressure appears in the oil absorption, the oil in the oil tank can be timely supplemented to the oil absorption side of the hydraulic pump 1 through the springless check valve, and meanwhile, the gear pump 2 connected in series is used as an oil supplementing pump, so that the oil absorption timeliness and the reliability of the hydraulic pump 1 are ensured. When the hydraulic cylinder 10 descends, load potential energy is mainly absorbed by the servo motor 3, the first balance valve 5.1 is only used for discharging oil of a rodless cavity of the hydraulic cylinder 10 during descending, and the second balance valve 5.2 does not throttle during working and does not bring extra throttling loss, so that energy waste can be greatly reduced under the condition that the load is rapidly erected. The deceleration and stopping at the time of load drop depend on the braking characteristics of the servo motor 3, and the deceleration and braking are smooth. The switch loop formed by the first two-way cartridge valve 6.1 and the second two-way cartridge valve 6.2 locks the load when the load is static and the swashplate swing angle of the hydraulic pump 1 returns to zero, so that the load is prevented from sliding down due to tiny leakage when the swashplate of the hydraulic pump 1 is in zero position. The two cavities of the hydraulic cylinder 10 are respectively connected with the first overflow valve 9.1 and the second overflow valve 9.2, so that the two cavities of the hydraulic cylinder 10 are effectively prevented from being blocked when the first two-way cartridge valve 6.1 and the second two-way cartridge valve 6.2 are opened and fail, and the loop safety is improved.
In combination with fig. 1, the reliability of the system is described as follows, after the center of gravity is raised, the hydraulic cylinder 10 is pulled at this time, the generated negative power is absorbed by the servo motor 3, the energy is dissipated through the braking resistor when the servo motor 3 works in a reverse dragging mode, and the servo motor 3 works in a generator mode and responds quickly. The flow control is realized by means of two modes of adjusting the rotating speed of the servo motor 3 and the displacement of the hydraulic pump 1. When the center of gravity is crossed, the servo motor 3 has a band-type brake function, if the servo motor 3 is in deceleration failure, the first switch S1 and the second switch S2 are powered off, the hydraulic cylinder 10 is locked, and safety and controllability are ensured. After the system fails or is powered off, the second throttle valve 8.2 is fully opened, the first throttle valve 8.1 is opened, and the speed of load lowering can be controlled by adjusting the opening of the first throttle valve 8.1.
Claims (5)
1. A closed pump control quick erection system is characterized in that: the hydraulic control system comprises a hydraulic pump (1), a gear pump (2), a servo motor (3), a first hydraulic control reversing valve (4.1), a second hydraulic control reversing valve (4.2), a first balance valve (5.1), a second balance valve (5.2), a first two-way cartridge valve (6.1), a second two-way cartridge valve (6.2), a first electromagnetic reversing valve (7.1), a second electromagnetic reversing valve (7.2), a first throttle valve (8.1), a second throttle valve (8.2), a first overflow valve (9.1), a second overflow valve (9.2) and a hydraulic cylinder (10);
The hydraulic pump (1), the gear pump (2) and the servo motor (3) are coaxially and sequentially connected; the hydraulic pump (1) is a variable displacement hydraulic pump, and a first interface A1 and a second interface A2 are arranged on the hydraulic pump; the hydraulic cylinder (10) is provided with a third interface A3 and a fourth interface A4, the second interface A2 of the hydraulic pump (1) is respectively communicated with an oil outlet of the gear pump (2), an interface A of the first hydraulic control reversing valve (4.1), an oil inlet of the first balance valve (5.1) and an interface A of the first two-way cartridge valve (6.1) through pipelines, the interface B of the first two-way cartridge valve (6.1) is respectively communicated with an interface P of the first electromagnetic reversing valve (7.1) through pipelines, an interface P of the first throttle valve (8.1), an oil inlet of the first overflow valve (9.1) and a third interface A3 of the hydraulic cylinder (10), the interface A1 of the hydraulic pump (1) is respectively communicated with the oil outlet of the gear pump (2), the interface A of the second hydraulic control reversing valve (4.2) through the one-way valve, the oil inlet of the second balance valve (5.2) and an interface A of the second two-way cartridge valve (6.2), the interface B of the second two-way cartridge valve (6.2) is respectively communicated with the interface P of the first electromagnetic reversing valve (7.1), the first throttle valve (2) through pipelines, the second electromagnetic reversing valve (9.1) and the oil outlet of the first hydraulic pump (2), the second electromagnetic valve (2) and the second electromagnetic reversing valve (8.1, the second electromagnetic reversing valve (2) through the interface A1, the interface T1, the first electromagnetic valve (2) and the oil outlet of the hydraulic pump (2) and the third interface A3 The oil outlet of the first balance valve (5.1), the oil outlet of the second balance valve (5.2), the interface C of the first hydraulic control reversing valve (4.1), the interface C of the second hydraulic control reversing valve (4.2) and the oil suction port of the gear pump (2) are respectively communicated with the oil tank, the interface A of the first electromagnetic reversing valve (7.1) is communicated with the interface X of the first two-way cartridge valve (6.1), the interface A of the second electromagnetic reversing valve (7.2) is communicated with the interface X of the second two-way cartridge valve (6.2), the interface B of the first hydraulic control reversing valve (4.1) is communicated with the pressure control port of the second balance valve (5.2), and the interface B of the second hydraulic control reversing valve (4.2) is communicated with the pressure control port of the first balance valve (5.1).
2. The closed pump control quick erection system of claim 1, wherein: the hydraulic pump (1) is driven by the servo motor (3), the expansion and contraction of the hydraulic cylinder (10) are completed by switching positive and negative inclination angles of a swash plate of the hydraulic pump (1), and the rotation speed of the servo motor (3) and the displacement of the hydraulic pump (1) jointly determine the output flow so as to control the expansion and contraction speed of the hydraulic cylinder (10); when the load is too heavy, the servo motor (3) is preferentially used for absorbing load potential energy, and when the load is lowered, the first balance valve (5.1) is used for guiding redundant flow into the oil tank, so that the hydraulic pump (1) has proper oil absorption and pressure oil flow when the hydraulic cylinder (10) stretches; the gear pump (2) plays a role in supplementing oil in the hydraulic circuit; for locking of the load, a switching loop composed of the first two-way cartridge valve (6.1) and the second two-way cartridge valve (6.2) is used for control, so that throttling loss caused by locking of the balance valve is avoided, and the load can be raised and lowered with higher efficiency.
3. The closed pump control quick erection system of claim 1, wherein the erection process is as follows:
The hydraulic pump (1) is adjusted to be at a positive swing angle, a first switch S1 of the first electromagnetic directional valve (7.1) and a second switch S2 of the second electromagnetic directional valve (7.2) are simultaneously electrified, the locking state of the hydraulic cylinder (10) is relieved, the rotating speed of the servo motor (3) is adjusted, a rodless cavity of the hydraulic cylinder (10) is filled with oil, and the load is increased; when the pressure of the rodless cavity is higher than the preset pressure P 1 of the first hydraulic control reversing valve (4.1), the pilot pressure of the second balance valve (5.2) is established and then is started, the flow pressure loss after the second balance valve (5.2) is conducted is the set pressure P 2 of the pilot pressure, at the moment, the rodless cavity side of the hydraulic pump (1) connected with the hydraulic cylinder (10) is in an oil absorption and oil supplementing stage through an oil tank, and the pressure loss of P 2 can enable oil to enter an oil inlet of the hydraulic pump (1) and not leak through the second balance valve (5.2); when the load rises to an overweight center position, under the action of the load, the hydraulic cylinder (10) generates negative thrust, when the load has the working condition of traction the hydraulic cylinder (10), the oil inlet side pressure of the hydraulic pump (1) can rise, the pressure oil side pressure is reduced, when the pressure oil side pressure is reduced below P1, the second balance valve (5.2) is closed, the oil liquid with a rod cavity of the hydraulic cylinder (10) under the negative thrust is prevented from leaking out through the second balance valve (5.2), the hydraulic cylinder (10) is further caused to be uncontrolled, and at the moment, the negative power generated under the negative thrust is absorbed by the servo motor (3); after the load rises to the top end, the first switch S1 and the second switch S2 are powered off, meanwhile, the rotating speed of the servo motor (3) is adjusted to 0 rpm, the inclined angle of a swash plate of the hydraulic pump (1) returns to the zero position, and the hydraulic cylinder (10) is locked by a switch loop formed by the first two-way cartridge valve (6.1) and the second two-way cartridge valve (6.2); when stopping at any position, the same procedure is performed.
4. The closed pump control quick erection system of claim 1, wherein the back-leveling process is as follows:
The hydraulic pump (1) is adjusted to a negative swing angle, the first switch S1 and the second switch S2 are powered on simultaneously, the locking state of the hydraulic cylinder (10) is relieved, the rotating speed of the servo motor (3) is adjusted, the hydraulic cylinder (10) is provided with a rod cavity for oil feeding, the load is reduced, and the oil discharge flow of the rodless cavity is larger than the oil feed flow of the rod cavity due to the existence of the area difference of the two cavities of the hydraulic cylinder (10), so that the hydraulic pump (1) can accept the oil discharge of the rodless cavity without oil supplementing; if the first balance valve (5.1) is not conducted, the redundant flow on the rodless cavity side of the hydraulic cylinder (10) can cause the pressure on the rod cavity side to rise, and when the pressure on the rod cavity side is higher than the pressure P3 of the preset second hydraulic control reversing valve (4.2), the first balance valve (5.1) establishes pilot pressure and then conducts, and the redundant flow leaks from the balance valve (5.1) to the oil tank; if the hydraulic cylinder (10) is out of control in the load descending process, the pressure of a rod cavity of the hydraulic cylinder (10) tends to be reduced or even negative pressure occurs, when the side pressure of the rod cavity is lower than P3, the first balance valve (5.1) is closed, the redundant flow of the rodless cavity side of the hydraulic cylinder (10) can cause the pressure of the rod cavity side to be increased, and meanwhile, the servo motor (3) can be reversely dragged by the hydraulic pump (1) to overspeed to form a braking effect, so that the out-of-control descending of the hydraulic cylinder (10) is prevented; after the load is lowered to the bottom end, the first switch S1 and the second switch S2 are powered off, meanwhile, the rotating speed of the servo motor (3) is adjusted to be 0rpm, the swashplate swing angle of the hydraulic pump (1) returns to the zero position, and the hydraulic cylinder (10) is locked by a switch loop formed by two through cartridge valves (6); when the lowering is stopped at an arbitrary position, the same procedure is performed.
5. The closed pump control quick erection system of claim 1, wherein: the hydraulic pump (1) can directly absorb oil from the oil tank while receiving the return oil of the system, and the gear pump (2) connected in series is used as a supplementary oil pump, so that the timeliness and reliability of oil absorption of the hydraulic pump (1) are ensured; when the hydraulic cylinder (10) descends, load potential energy is mainly absorbed by the servo motor (3), and the deceleration and stopping during the load descending depend on the braking characteristic of the servo motor (3), so that the deceleration and braking are stable; the load is locked when the load is static and the swashplate swing angle of the hydraulic pump (1) returns to zero by a switch loop formed by the first two-way cartridge valve (6.1) and the second two-way cartridge valve (6.2), so that the load is prevented from sliding down due to tiny leakage when the swashplate of the hydraulic pump (1) is in zero position; after the system fails or is powered off, the second throttle valve (8.2) is fully opened, the first throttle valve (8.1) is opened, and the speed of load discharging can be controlled by adjusting the opening degree of the first throttle valve (8.1).
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| CN204061372U (en) * | 2014-08-11 | 2014-12-31 | 徐州工业职业技术学院 | A kind of oil hydraulic cylinder quick-expansion control loop |
| CN204312429U (en) * | 2014-11-24 | 2015-05-06 | 番禺珠江钢管有限公司 | A kind of hydraulic differential circuit system be made up of screw-in cartridge valve |
| CN206320089U (en) * | 2016-12-23 | 2017-07-11 | 南京埃斯顿自动化股份有限公司 | Hydraulic control system based on electro-hydraulic servo type hydraulic press |
| JP2018145984A (en) * | 2017-03-01 | 2018-09-20 | 株式会社日立建機ティエラ | Hydraulic transmission for construction machine |
| CN211288284U (en) * | 2019-09-25 | 2020-08-18 | 四川宏华石油设备有限公司 | Hydraulic device |
| CN111810472A (en) * | 2020-08-12 | 2020-10-23 | 辽宁忠旺机械设备制造有限公司 | Load-sensitive control loop based on load sensing pump and Vaivistor valve |
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| CN114278624A (en) | 2022-04-05 |
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