CN114278624A - Closed pump control system of erecting fast - Google Patents
Closed pump control system of erecting fast Download PDFInfo
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Abstract
The invention discloses a closed pump control quick erecting system, which uses a servo motor to drive a hydraulic pump, wherein the reversing of a hydraulic cylinder is completed by switching the positive and negative inclination angles of a swash plate of the hydraulic pump, and the rotating speed of the servo motor and the displacement of the hydraulic pump jointly determine the output flow so as to control the ascending and descending speeds of the hydraulic cylinder; when the load exceeds the gravity center, the servo motor can absorb the load potential energy, when the load descends, the balance valve guides redundant flow into the oil tank, and the hydraulic pump is ensured to have proper oil absorption and oil pressing flow when the hydraulic cylinder ascends and descends. The gear pump plays a role in oil supplement in the system; for the locking of the load, a switching loop formed by the cartridge valves is used for controlling, so that the throttling loss caused by the locking of the balance valve is avoided, and the load is enabled to rise and fall and has high hydraulic efficiency. The closed hydraulic circuit provided by the invention overcomes the defects of the traditional valve control 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 type pump control quick erecting system.
Background
With the great development of the engineering machinery industry in China, the method has important significance for effectively reducing the energy consumption in the process of loading and erecting. In the process of erecting the load, the hydraulic drive realizes large-scale energy transfer by utilizing hydraulic pressure storage pressure energy, generates huge thrust and is very suitable for heavy-load operation working conditions such as large engineering machinery. In the 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 finally reaches a hydraulic cylinder to push a load through various control valves and finally returns to the oil tank, and the pressure of a system and the speed and direction of an actuating mechanism are controlled by various hydraulic valves. Guoshao discloses a multi-cylinder collaborative erecting hydraulic system, which adopts an open valve control erecting loop to control a double-acting hydraulic cylinder, obviously improves erecting speed and leveling speed, shortens launching time, but is more complex, thereby leading to larger integral volume of the hydraulic system and larger throttling loss in erecting and leveling processes. The open valve-controlled quick erecting system has obvious defects that firstly, oil is easy to leak, when hydraulic oil passes through various valves, the leakage of the oil is easy to generate due to possible sealing failure at the interface of a pipeline and the valve, and potential safety hazards exist in the process of erecting a load; secondly, the efficiency problem is that in the whole hydraulic system, the loss of a general servo motor and a general hydraulic pump accounts for about 10%, the loss of a hydraulic valve is 40% -60%, the loss of the hydraulic valve finally reaches only 30% -50% of an actuating mechanism, and the efficiency is low; and thirdly, the volume of the whole hydraulic system is large, and all elements in the traditional hydraulic system need to be connected through pipelines, so that the volume of the hydraulic system is increased, the space is occupied, and the load is increased.
Disclosure of Invention
The invention aims to provide a closed pump-controlled quick erecting system which can realize quick erecting of a load and has the characteristics of higher efficiency, smaller volume and lighter weight compared with a traditional open valve-controlled hydraulic system.
The technical solution for realizing the purpose of the invention is as follows: the utility model provides a closed pump accuse system of erectting fast, includes hydraulic pump, gear pump, servo motor, first hydraulic control switching-over valve, second hydraulic control switching-over valve, first balanced valve, second balanced valve, first two-way cartridge valve, second two-way cartridge valve, first electromagnetic directional valve, second electromagnetic directional valve, first choke valve, second choke valve, first overflow valve, second overflow valve, pneumatic cylinder.
The oil tank is designed mainly by considering the volume difference of the positive cavity and the negative cavity of the hydraulic cylinder, so that the oil tank plays a role in supplementing oil. The hydraulic pump is a variable pump, and the servo motor is directly connected with the hydraulic pump and used as a power source of the 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 volume difference of the positive cavity and the negative cavity of the hydraulic cylinder, thereby playing the role of oil supplement
All the valve elements can be integrated into one hydraulic valve block without complex pipeline connection. 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 following remarkable advantages: adopt closed circuit design, based on the principle of "electricity drive liquid and pass" to servo motor drive hydraulic pump, the hydraulic pump passes through integrated valve block drive pneumatic cylinder, and the switching-over of pneumatic cylinder is accomplished by the positive negative inclination of switching hydraulic pump sloping cam plate, constitutes fluid drive closed circulation, has the advantage of traditional hydraulic drive and direct electric drive actuator concurrently, externally only includes power supply interface and mechanical installation interface. The use of the hydraulic self-locking module and the unloading module improves the safety to the maximum extent. The hydraulic system can realize that the vertical erecting time of the load is shorter, and meanwhile, the erecting process is stable and reliable, 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-controlled fast-erecting hydraulic system of the present invention.
Detailed Description
The present invention will be described in further detail with reference to fig. 1 and the following embodiments.
With reference to fig. 1, a closed pump-controlled fast erecting system comprises a hydraulic pump 1, a gear pump 2, a servo motor 3, a first hydraulic control directional control valve 4.1, a second hydraulic control directional control 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 directional control valve 7.1, a second electromagnetic directional control 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 port A1 and a second port A2. The hydraulic cylinder 10 is provided with a third interface A3 and a fourth interface A4, a 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 a one-way valve, a 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, an interface A 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 through pipelines, an interface A1 of the hydraulic pump 1 is respectively communicated with an oil outlet of the gear pump 2, an interface A of the second hydraulic control reversing valve 4.2, an oil inlet of the second balance valve 5.2 and an interface A of the second two-way cartridge valve 6.2 through a one-way valve, and an interface B of the second two-way cartridge valve 6.2 is respectively communicated with an interface P of the second electromagnetic reversing valve 7.2, an interface P of the second throttle valve 8.2, an interface A4 and an oil inlet of the second overflow valve 9.2 through pipelines, The fourth port A4 of the hydraulic cylinder 10 is communicated, the first port A1 of the hydraulic pump 1 is communicated with the first port T of the first electromagnetic directional valve 7.1 through a one-way valve, a first throttle valve 8.1 port, a second throttle valve 8.2 port, an oil outlet of a first overflow valve 9.1, an oil outlet of a second overflow valve 9.2, the interface T of the second electromagnetic directional valve 7.2, 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 directional valve 4.1, the interface C of the second hydraulic control directional valve 4.2 and the oil suction port of the gear pump 2 are respectively communicated with an oil tank, the interface A of the first electromagnetic directional 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 directional 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 directional 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 directional valve 4.2 is communicated with the pressure control port of the first balance valve 5.1.
The closed type pump control quick erecting hydraulic system uses the servo motor 3 to drive the hydraulic pump 1, the reversing of the hydraulic cylinder 10 is completed by switching the positive and negative inclination angles of the swash plate of the hydraulic pump 1, and the rotating 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 speed of the hydraulic cylinder 10. The gear pump 2 plays a role in oil supplement in the system. All valve components can be integrated into one hydraulic valve block, and complex 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, a symmetrical oil way is used for responding to the flow change of oil discharged by the asymmetrical hydraulic cylinder 10, the servo motor 3 is preferentially considered to absorb load potential energy when the gravity center is exceeded, and the balance valve 5.1 is used for guiding redundant flow into an oil tank when the load descends, so that the hydraulic pump 1 is ensured to have proper oil absorption and oil pressing flow when the hydraulic cylinder 10 ascends and descends. The gear pump 2 serves as an oil supply in the hydraulic circuit. For locking of the load, a switch loop formed by the first two-way cartridge valve 6.1 and the second two-way cartridge valve 6.2 is used for controlling, throttling loss caused by locking of the load by using a balance valve in a traditional erecting system is avoided, and the load is enabled to rise and fall and has high hydraulic efficiency.
With reference to fig. 1, the operation process of the hydraulic system is described as follows, when a load rises, the hydraulic pump 1 is adjusted to be at 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 rotation speed of the servo motor 3 is adjusted, oil is fed into a rodless cavity of the hydraulic cylinder 10, and the load rises. The pressure of the rodless cavity is higher than the set pressure P of the first hydraulic control reversing valve 4.11When the pressure is higher than the preset pressure P, the second balance valve 5.2 is opened after the pilot pressure is built, and the flow pressure loss after the second balance valve 5.2 is conducted is the preset pressure P2At the moment, the rodless cavity side of the hydraulic pump 1 connected with the hydraulic cylinder 10 is in the oil absorption and oil supplement stage through an oil tank, P2The pressure loss of (2) causes the oil to enter the oil inlet of the hydraulic pump 10 without leaking out through the second balance valve 5.2. When the load rises to the position of over gravity center, the hydraulic cylinder 10 generates negative thrust under the action of the load, and when the working condition of pulling the hydraulic cylinder 10 is loaded, the oil inlet side pressure of the hydraulic pump 1 is caused to rise, the pressure of the oil pressure side is reduced, and when the pressure of the oil pressure side is reduced to P1When the negative thrust is applied, the second balance valve 5.2 is closed to prevent the oil liquid in the rod cavity of the hydraulic cylinder 10 under the negative thrust from leaking out through the second balance valve 5.2, so that the hydraulic cylinder 10 is not controlled, and the negative thrust is applied at the momentThe negative power generated in the lower stage is absorbed by the servomotor 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 inclination angle of the swash plate of the hydraulic pump 1 returns to a zero position, and the hydraulic cylinder 10 is locked by a switch loop consisting of the first two-way cartridge valve 6.1 and the second two-way cartridge valve 6.2. When stopping at any position, the process is the same. When the load descends, the hydraulic pump 1 is adjusted to be at 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, oil is fed into the rod cavity of the hydraulic cylinder 10, the load descends, due to the fact that the area difference of the two cavity surfaces of the hydraulic cylinder 10 exists, the oil discharge flow of the rodless cavity is larger than the oil feed flow of the rod cavity, and the hydraulic pump 1 can receive oil discharged from the rodless cavity without oil supplement from an oil tank. The flow difference exists between the two cavities in the descending process of the hydraulic cylinder 10, 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 the pressure on the rod cavity side is higher than the set pressure P of the second hydraulic control reversing valve 4.23When the pilot pressure is built up, the first balance valve 5.1 is conducted, and redundant flow is discharged to the oil tank from the first balance valve 5.1. If the hydraulic cylinder 10 is out of control in the process of load descending, the pressure of the rod cavity of the hydraulic cylinder 10 is liable to descend and even generates negative pressure, and the side pressure of the rod cavity is lower than P3When this happens, the first balancing valve 5.1 is closed and the servomotor 3 will be dragged by the hydraulic pump 1 against the braking effect of the overspeed, thus preventing uncontrolled lowering of the hydraulic cylinder 10. 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 swing angle of the swash plate of the hydraulic pump 1 returns to a 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 of the descent, the same procedure is performed.
With reference to fig. 1, the system safety is described as follows, and in a closed circuit, sufficient oil supplement and timeliness of oil supplement of a hydraulic pump are the prerequisites for ensuring safe operation of the hydraulic pump. In the loop, the oil suction of the hydraulic pump 1 not only receives system return oil, but also can directly suck oil from the oil tank, if the oil suction side has positive pressure, the condition that the hydraulic pump 1 has reliable oil suction is shown, the reed-free one-way valve can separate the oil suction ports of the oil tank and the hydraulic pump 1, pressure oil on the oil suction side is prevented from entering the oil tank, once negative pressure occurs in oil suction, oil in the oil tank can be timely supplemented to the oil suction side of the hydraulic pump 1 through the reed-free one-way valve, and meanwhile, the gear pump 2 which is connected in series serves as an oil supplementing pump, so that the timeliness and the reliability of oil suction of the hydraulic pump 1 are guaranteed. 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 oil discharge of a rodless cavity of the hydraulic cylinder 10 when the hydraulic cylinder descends, and the second balance valve 5.2 does not throttle when working, so that extra throttling loss is avoided, and therefore energy waste can be greatly reduced under the condition that the load is erected quickly. The deceleration and stop when the load is lowered depend on the braking characteristics of the servo motor 3, and the deceleration and the braking are smooth. A 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 swing angle of the swash plate of the hydraulic pump 1 returns to zero, so that the load is prevented from sliding downwards due to tiny leakage when the swash plate of the hydraulic pump 1 returns to zero. 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 suppressed when the first two-way cartridge valve 6.1 and the second two-way cartridge valve 6.2 are opened and fail, and the safety of a loop is improved.
With reference to fig. 1, the system reliability is described as follows, after the vertical center of gravity is passed, 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 brake resistor when the servo motor 3 works in a reverse drag mode, and the servo motor 3 works in a generator mode and has a fast response. Flow control is realized by adjusting the rotating speed of the servo motor 3 and the displacement of the hydraulic pump 1. When the gravity center is crossed, the servo motor 3 has a brake function, if the servo motor 3 fails to decelerate, the first switch S1 and the second switch S2 are powered off, the hydraulic cylinder 10 is locked, and safety and controllability are guaranteed. After the system is in fault or power failure, the second throttle valve 8.2 is fully opened, the first throttle valve 8.1 is opened again, and the speed of load lowering can be controlled by adjusting the opening of the first throttle valve 8.1.
Claims (5)
1. The utility model provides a system is erected fast to closed pump accuse which characterized in that: the hydraulic control system comprises a hydraulic pump (1), a gear pump (2), a servo motor (3), a first hydraulic control directional valve (4.1), a second hydraulic control directional 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 directional valve (7.1), a second electromagnetic directional 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) and the gear pump (2) are coaxially and sequentially connected with the servo motor (3); the hydraulic pump (1) is a variable displacement hydraulic pump, and a first port A1 and a second port A2 are arranged on the hydraulic pump; the hydraulic cylinder (10) is provided with a third connector A3 and a fourth connector A4, a second connector A2 of the hydraulic pump (1) is communicated with an oil outlet of the gear pump (2), a connector A of the first hydraulic control reversing valve (4.1), an oil inlet of the first balance valve (5.1) and a connector A of the first two-way cartridge valve (6.1) through a one-way valve respectively, a connector B of the first two-way cartridge valve (6.1) is communicated with a connector P of the first electromagnetic reversing valve (7.1), a connector of the first throttle valve (8.1), an oil inlet of the first overflow valve (9.1) and a third connector A3 of the hydraulic cylinder (10) through pipelines respectively, the connector A1 of the hydraulic pump (1) is communicated with an oil outlet of the gear pump (2), a connector A of the second hydraulic control reversing valve (4.2), an oil inlet of the second balance valve (5.2) and a connector A of the second balance valve (6.2) through a one-way valve (6.2) and the second two-way cartridge valve (6.2) is communicated with a connector P of the electromagnetic reversing valve (7.2) through a connector B) and a pipeline respectively, A second throttle valve (8.2) interface, a second overflow valve (9.2) oil inlet and a fourth interface A4 of the hydraulic cylinder (10) are communicated, a first interface A1 of the hydraulic pump (1) is communicated with an oil outlet of the second overflow valve (9.2) through a one-way valve, a first throttle valve (8.1) interface, a second throttle valve (8.2) interface, an oil outlet of the first overflow valve (9.1), an oil outlet of the second overflow valve (9.2), an interface T of the first electromagnetic directional valve (7.1), an interface T of the second electromagnetic directional valve (7.2), an oil outlet of the first balance valve (5.1), an oil outlet of the second balance valve (5.2), an interface C of the first hydraulic directional valve (4.1), an interface C of the second hydraulic directional valve (4.2) and an oil suction port of the gear pump (2), an interface A of the first electromagnetic directional valve (7.1) is communicated with an interface X of the first two-way cartridge valve (6.1), and an interface A of the second electromagnetic directional valve (7.2) is communicated with an interface X of the second 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-controlled fast erecting system as recited in claim 1 further comprising: the hydraulic pump (1) is driven by the servo motor (3), the hydraulic cylinder (10) is stretched by the positive and negative inclination angles of the swash plate switched by 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 stretching speed of the hydraulic cylinder (10); when the gravity center is exceeded, the servo motor (3) is preferentially considered to absorb load potential energy, and when the load is reduced, the first balance valve (5.1) is used for guiding redundant flow into an oil tank, so that the hydraulic pump (1) is ensured to have proper oil absorption and oil pressing flow when the hydraulic cylinder (10) is stretched; the gear pump (2) plays a role in oil supplement in a hydraulic circuit; for locking of the load, a switching circuit consisting of the first two-way cartridge valve (6.1) and the second two-way cartridge valve (6.2) is used for controlling, throttling loss caused by locking of a balance valve is avoided, and the load is enabled to rise and fall at the same time to have high efficiency.
3. The closed pump-controlled fast erecting system according to claim 1, wherein the erecting process is as follows:
the hydraulic pump (1) is adjusted to be at a positive swing angle, a first switch S1 of a first electromagnetic directional valve (7.1) and a second switch S2 of a second electromagnetic directional valve (7.2) are powered on simultaneously, the locking state of the hydraulic cylinder (10) is released, the rotating speed of the servo motor (3) is adjusted, oil is fed into a rodless cavity of the hydraulic cylinder (10), and the load rises; the pressure of the rodless cavity is higher than the preset pressure P of the first hydraulic control reversing valve (4.1)1When the pressure is higher than the set pressure P, the second balance valve (5.2) is opened after the pilot pressure is built, and the flow pressure loss after the second balance valve (5.2) is conducted is the set pressure P2At the moment, the side of the rodless cavity of the hydraulic pump (1) connected with the hydraulic cylinder (10) is in the oil absorption and oil supplement stage through an oil tank, P2The pressure loss can lead the oil to enter an oil inlet of the hydraulic pump (1) and not to leak out through the second balance valve (5.2); when the load rises to the position of over gravity center, the hydraulic cylinder (10) generates negative thrust under the action of the load, and when the load has the working condition of drawing the hydraulic cylinder (10), the oil inlet side pressure of the hydraulic pump (1) is caused to rise, the pressure oil side pressure is caused to fall, and the pressure is required to be pressedWhen the pressure on the oil side is reduced to be below P1, the second balance valve (5.2) is closed, so that the oil in the rod cavity of the hydraulic cylinder (10) under the negative thrust is prevented from leaking out through the second balance valve (5.2), and the hydraulic cylinder (10) is further uncontrolled, and 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, the rotating speed of the servo motor (3) is adjusted to 0rpm, the inclination angle of the swash plate of the hydraulic pump (1) returns to the zero position, and the hydraulic cylinder (10) is locked by a switch loop consisting of the first two-way cartridge valve (6.1) and the second two-way cartridge valve (6.2); when stopping at any position, the process is the same.
4. The closed pump-controlled fast erecting system of claim 1 wherein the leveling back process is as follows:
the hydraulic pump (1) is adjusted to be at 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, oil is fed into a rod cavity of the hydraulic cylinder (10), the load is reduced, and due to the fact that the area difference of two cavity surfaces of the hydraulic cylinder (10) exists, the oil discharge flow of the rodless cavity is larger than the oil feed flow of the rod cavity at the moment, and the hydraulic pump (1) can receive the oil discharged from the rodless cavity without oil supplement; flow difference exists between the two cavities in the descending process of the hydraulic cylinder (10), if the first balance valve (5.1) is not conducted, redundant flow on the rodless cavity side of the hydraulic cylinder (10) causes pressure on the rod cavity side to rise, when the pressure on the rod cavity side is higher than pressure P3 of the preset second hydraulic control reversing valve (4.2), the first balance valve (5.1) is conducted after pilot pressure is built, and redundant flow is drained to an oil tank from the balance valve (5.1); if the hydraulic cylinder (10) is out of control in the process of load descending, the pressure of a rod cavity of the hydraulic cylinder (10) tends to descend 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) causes the pressure of the rod cavity side to rise, and meanwhile, the servo motor (3) is dragged by the hydraulic pump (1) to form a braking effect due to overspeed, 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 0rpm, the swing angle of a swash plate of the hydraulic pump (1) returns to a zero position, and the hydraulic cylinder (10) is locked by a switch loop formed by the two-way cartridge valve (6); when stopping at any position of the descent, the same procedure is performed.
5. The closed pump-controlled fast erecting system as recited in claim 1 further comprising: the hydraulic pump (1) can directly absorb oil from the oil tank while receiving system return oil, and the gear pumps (2) connected in series are used as oil supplementing pumps, 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 the stop of the descending load depend on the braking characteristic of the servo motor (3), so that the deceleration and the braking are stable; a 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 swash plate swing angle of the hydraulic pump (1) returns to zero, so that the load is prevented from sliding downwards due to tiny leakage when the swash plate of the hydraulic pump (1) is in a zero position; after the system is in fault or power failure, the second throttle valve (8.2) is fully opened, the first throttle valve (8.1) is opened again, and the speed of load lowering can be controlled by adjusting the opening of the first throttle valve (8.1).
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Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1800654A (en) * | 2005-12-20 | 2006-07-12 | 武汉科技大学 | Asymmetric cylinder closed-loop speed system controlled by electro-hydraulic proportional pump |
| 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 |
-
2021
- 2021-12-10 CN CN202111510477.0A patent/CN114278624B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1800654A (en) * | 2005-12-20 | 2006-07-12 | 武汉科技大学 | Asymmetric cylinder closed-loop speed system controlled by electro-hydraulic proportional pump |
| 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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| CN114278624B (en) | 2024-05-03 |
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