CN113494488B - Hydraulic control valve group and servo valve control cylinder system - Google Patents

Hydraulic control valve group and servo valve control cylinder system Download PDF

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Publication number
CN113494488B
CN113494488B CN202010262951.1A CN202010262951A CN113494488B CN 113494488 B CN113494488 B CN 113494488B CN 202010262951 A CN202010262951 A CN 202010262951A CN 113494488 B CN113494488 B CN 113494488B
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oil
valve
hydraulic
port
self
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CN113494488A (en
Inventor
杨永立
张文全
刘丹
李俊
刘延龙
邓亮
华宁
苏荣荣
谢建云
李乐超
陈瑶
陈昊
黄莉
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Guangdong Bozhilin Robot Co Ltd
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Guangdong Bozhilin Robot Co Ltd
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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
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/021—Installations or systems with accumulators used for damping
    • 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
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • 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
    • F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
    • 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
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • 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
    • F15B2211/86—Control during or prevention of abnormal conditions
    • F15B2211/8606—Control during or prevention of abnormal conditions the abnormal condition being a shock
    • 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

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

Abstract

The application provides a hydraulic control valve group and a servo valve cylinder control system. A hydraulic control valve block comprising: the self-locking module is connected with the hydraulic oil cylinder; the self-locking control module is respectively connected with the hydraulic oil source and the self-locking module and is used for controlling the opening and closing of the self-locking module; when the self-locking module is opened, the hydraulic oil cylinder is in a self-locking state; and when the self-locking module is closed, an oil way between the hydraulic oil cylinder and the hydraulic oil source is communicated. The hydraulic control valve group is used for ensuring the quick response characteristic of a servo valve control cylinder system and improving the working efficiency of the system.

Description

Hydraulic control valve group and servo valve control cylinder system
Technical Field
The application relates to the technical field of automatic control, in particular to a hydraulic control valve group and a servo valve control cylinder system.
Background
In a servo valve cylinder control system, a self-locking module is generally arranged and used for keeping a hydraulic oil cylinder in a self-locking state when the hydraulic oil cylinder needs to be locked. However, in the conventional arrangement, the self-locking module is not controllable, and may be frequently opened and closed due to the state change of the oil passage, thereby affecting the quick response characteristics of the system (such as short positioning time, high positioning accuracy, and the like), and reducing the working efficiency of the system.
Disclosure of Invention
An object of the embodiment of the present application is to provide a hydraulic control valve group and a servo valve cylinder control system, so as to ensure the quick response characteristic of the servo valve cylinder control system and improve the work efficiency of the system.
In a first aspect, an embodiment of the present application provides a hydraulic control valve group, including: the self-locking module is connected with the hydraulic oil cylinder; the self-locking control module is respectively connected with the hydraulic oil source and the self-locking module and is used for controlling the opening and closing of the self-locking module; when the self-locking module is opened, the hydraulic oil cylinder is in a self-locking state; and when the self-locking module is closed, an oil way between the hydraulic oil cylinder and the hydraulic oil source is communicated.
In the embodiment of the application, in the hydraulic control valve bank, the self-locking control module is arranged for the self-locking module, the self-locking control module can control the opening and closing of the self-locking module, and when the self-locking module is opened, the hydraulic oil cylinder is in a self-locking state and cannot be influenced; when the self-locking module is closed, an oil way between the hydraulic oil cylinder and the hydraulic oil source is communicated, so that the normal operation of the oil way is ensured. Compared with the prior art, the self-locking module is not frequently opened or closed any more, but selectively opened or closed according to the control of the self-locking control module, so that the influence on the quick response characteristic of a system where the hydraulic control valve group is located is avoided, and the working efficiency of the system is improved.
As a possible implementation, the self-locking module includes: a first counter-balance valve and a second counter-balance valve; the first oil port of the first balance valve is connected with the rodless cavity of the hydraulic oil cylinder, and the first oil port of the second balance valve is connected with the rod cavity of the hydraulic oil cylinder; the self-locking control module comprises: lead oily module, include: the oil inlet is connected with the oil inlet; the first oil inlet is connected with a second oil port of the first balance valve, and the second oil inlet is connected with a second oil port of the second balance valve; the oil outlet is connected with the pilot oil ports of the first balance valve and the second balance valve; an oil port A of the servo valve is connected with a second oil port of the first balance valve, and an oil port B of the servo valve is connected with a second oil port of the second balance valve; an oil port P of the servo valve is also connected with an oil outlet of the oil guide module; an oil port B of the two-position four-way electromagnetic reversing valve is connected with an oil port P of the servo valve, and an oil port T of the two-position four-way electromagnetic reversing valve is connected with an oil port T of the servo valve; and an oil port P and an oil port T of the two-position four-way reversing valve are also connected with the hydraulic oil source.
In this embodiment, when the self-locking module includes the balance valve, the self-locking control module may realize the self-locking control function of the balance valve through the oil guiding module, the servo valve, and the two-position four-way electromagnetic directional valve. In the self-locking control module, different oil circuit conduction states can be realized through different conduction states of the servo valve and the two-position four-way electromagnetic directional valve, so that the opening and closing of the balance valve can be effectively controlled, and the influence on the quick response characteristic of a system caused by frequent opening and closing of the balance valve is avoided.
As a possible implementation, the oil guiding module includes: a first check valve and a second check valve; an oil inlet of the first check valve is connected with a second oil port of the first balance valve, and an oil inlet of the second check valve is connected with a second oil port of the second balance valve; the oil outlet of the first one-way valve is connected with the oil outlet of the second one-way valve and serves as the oil outlet of the oil guide module.
In this embodiment, the oil guiding module may include two check valves, oil inlets of the two check valves are oil inlets of the oil guiding module, and after the two oil outlets are connected, the two oil inlets are used as oil outlets of the oil guiding module, and may further guide oil for a pilot oil port of the balance valve, so as to effectively control opening and closing of the balance valve.
As a possible implementation, the oil guiding module is a shuttle valve.
In this application embodiment, the oil guiding module may also be directly a shuttle valve, the shuttle valve has two oil inlets and an oil outlet, the oil outlet is connected with the pilot oil port of the balance valve, and further, the oil guiding module may guide oil for the pilot oil port of the balance valve, so as to effectively control the opening and closing of the balance valve.
As a possible implementation, the hydraulic oil source includes: the energy accumulator is connected with the oil port P of the two-position four-way electromagnetic directional valve; one end of the overflow valve is connected with an oil port P of the two-position four-way electromagnetic reversing valve, and the other end of the overflow valve is connected with an oil port T of the two-position four-way electromagnetic reversing valve; an oil outlet of the third one-way valve is connected with an oil port P of the two-position four-way electromagnetic directional valve; the hydraulic pump is connected with an oil inlet of the third one-way valve; and the oil tank is connected with the hydraulic pump.
In the embodiment of the application, the hydraulic oil source consisting of the energy accumulator, the overflow valve, the one-way valve, the hydraulic pump and the oil tank can avoid generating overhigh pressure during oil supply, and further realize pressure maintaining and controlling of the system.
In a second aspect, an embodiment of the present application provides a servo valve controlled cylinder system, including: the hydraulic oil system comprises a hydraulic oil cylinder, a hydraulic oil source and a hydraulic control valve group; wherein, the hydraulic control valve group includes: the self-locking module is connected with the hydraulic oil cylinder; the self-locking control module is respectively connected with the hydraulic oil source and the self-locking module and is used for controlling the opening and closing of the self-locking module; when the self-locking module is opened, the hydraulic oil cylinder is in a self-locking state; and when the self-locking module is closed, an oil way between the hydraulic oil cylinder and the hydraulic oil source is communicated.
In the embodiment of the application, in the hydraulic control valve group of the servo valve cylinder control system, the self-locking control module is arranged for the self-locking module, the self-locking control module can control the opening and closing of the self-locking module, and when the self-locking module is opened, the hydraulic oil cylinder is in a self-locking state and cannot be influenced; when the self-locking module is closed, an oil way between the hydraulic oil cylinder and the hydraulic oil source is communicated, so that the normal operation of the oil way is ensured. Compared with the prior art, the self-locking module is not frequently opened or closed any more, but is selectively opened or closed according to the control of the self-locking control module, so that the influence on the quick response characteristic of the system is avoided, and the working efficiency of the system is improved.
As a possible implementation, the servo valve cylinder control system includes a plurality of hydraulic oil cylinders and a plurality of hydraulic control valve groups; the number of the hydraulic oil cylinders is the same as that of the hydraulic control valve groups; each hydraulic control valve group is connected with one hydraulic oil cylinder, and the hydraulic control valve groups connected with different hydraulic oil cylinders are connected with the hydraulic oil source.
In the embodiment, when a plurality of hydraulic oil cylinders are provided, a plurality of corresponding hydraulic control valve groups can be arranged, so that the self-locking module corresponding to each hydraulic oil cylinder is controllable, the influence on the quick response characteristic of the system is avoided, and the working efficiency of the system is improved.
As a possible implementation manner, the servo valve control cylinder system comprises a first hydraulic oil cylinder and a second hydraulic oil cylinder; the hydraulic control valve group comprises a first hydraulic control valve group and a second hydraulic control valve group; the first hydraulic control valve group is respectively connected with the first hydraulic oil cylinder and the hydraulic oil source; and the second hydraulic control valve group is respectively connected with the second hydraulic oil cylinder and the hydraulic oil source.
In this application embodiment, when there are two hydraulic cylinder, correspond and set up two hydraulic control valves, improve the work efficiency of system.
As a possible implementation, the self-locking module includes: a first counter-balance valve and a second counter-balance valve; the first oil port of the first balance valve is connected with the rodless cavity of the hydraulic oil cylinder, and the first oil port of the second balance valve is connected with the rod cavity of the hydraulic oil cylinder; the auto-lock control module includes: lead oily module, include: the oil inlet is connected with the oil inlet; the first oil inlet is connected with a second oil port of the first balance valve, and the second oil inlet is connected with a second oil port of the second balance valve; the oil outlet is connected with the pilot oil ports of the first balance valve and the second balance valve; an oil port A of the servo valve is connected with a second oil port of the first balance valve, and an oil port B of the servo valve is connected with a second oil port of the second balance valve; an oil port P of the servo valve is also connected with an oil outlet of the oil guide module; an oil port B of the two-position four-way electromagnetic reversing valve is connected with an oil port P of the servo valve, and an oil port T of the two-position four-way electromagnetic reversing valve is connected with an oil port T of the servo valve; and an oil port P and an oil port T of the two-position four-way reversing valve are also connected with the hydraulic oil source.
As a possible implementation, the hydraulic oil source includes: the energy accumulator is connected with the oil port P of the two-position four-way electromagnetic directional valve; one end of the overflow valve is connected with an oil port P of the two-position four-way electromagnetic reversing valve, and the other end of the overflow valve is connected with an oil port T of the two-position four-way electromagnetic reversing valve; an oil outlet of the third one-way valve is connected with an oil port P of the two-position four-way electromagnetic directional valve; the hydraulic pump is connected with an oil inlet of the third one-way valve; and the oil tank is connected with the hydraulic pump.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings that are required to be used in the embodiments of the present application will be briefly described below, it should be understood that the following drawings only illustrate some embodiments of the present application and therefore should not be considered as limiting the scope, and that those skilled in the art can also obtain other related drawings based on the drawings without inventive efforts.
FIG. 1 is a schematic structural diagram of a servo valve cylinder control system according to an embodiment of the present disclosure;
FIG. 2 is an exemplary schematic diagram of a servo valve cylinder control system according to an embodiment of the present disclosure.
Icon: 10-a servo valve cylinder control system; 11-a hydraulic oil cylinder; 12-a source of hydraulic oil; 13-hydraulic control valve group; 130-self-locking module; 132-self-locking control module.
Detailed Description
The technical solutions in the embodiments of the present application will be described below with reference to the drawings in the embodiments of the present application.
Referring to fig. 1, which is a schematic structural diagram of a servo valve cylinder control system 10 according to an embodiment of the present disclosure, the servo valve cylinder control system 10 includes: hydraulic cylinder 11, hydraulic oil source 12 and hydraulic control valve group 13.
Wherein, hydraulic control valve group 13 includes: a self-locking module 130 and a self-locking control module 132. And the self-locking module 130 is connected with the hydraulic oil cylinder 11. The self-locking control module 132 is respectively connected with the hydraulic oil source 12 and the self-locking module 130 and is used for controlling the opening and closing of the self-locking module 130; when the self-locking module 130 is opened, the hydraulic oil cylinder 11 is in a self-locking state; when the self-locking module 130 is closed, the oil path between the hydraulic oil cylinder 11 and the hydraulic oil source 12 is conducted.
In the embodiment of the present application, in the hydraulic control valve group 13 of the servo valve cylinder control system 10, by providing the self-locking control module 132 for the self-locking module 130, the self-locking control module 132 can control the opening and closing of the self-locking module 130, and when the self-locking module 130 is opened, the hydraulic cylinder 11 is in a self-locking state and is not affected; when the self-locking module 130 is closed, the oil path between the hydraulic oil cylinder 11 and the hydraulic oil source 12 is conducted, so that the normal operation of the oil path is ensured. Compared with the prior art, the self-locking module 130 is not opened or closed frequently any more, but is selectively opened or closed according to the control of the self-locking control module 132, so that the influence on the quick response characteristic of the servo valve control cylinder system 10 is avoided, and the working efficiency of the servo valve control cylinder system 10 is improved.
In order to facilitate understanding of the technical solutions provided in the embodiments of the present application, the following describes embodiments of each module in the hydraulic control valve group 13.
For the self-locking module 130, it may include: a first counter-balance valve and a second counter-balance valve. The balance valve comprises three oil ports (a first oil port, a second oil port and a pilot oil port), under a normal condition (when the pilot oil port does not have high-pressure oil), the oil path of the hydraulic oil from the second oil port to the first oil port (connected with the hydraulic oil cylinder 11) is conducted, and the pressure at the moment is far larger than the load force during static. When the pilot oil port has high-pressure oil, the first oil port and the second oil port can be forced to be conducted, the balance valve is enabled to be completely opened, and the hydraulic oil can be conducted from the first oil port to the oil path of the second oil port. And, the balanced valve still has the pressure regulating and prevents the function of transshipping, can set for pressure according to actual demand. Further, the first oil port of the first balance valve is connected with the rodless cavity of the hydraulic oil cylinder 11, and the first oil port of the second balance valve is connected with the rod cavity of the hydraulic oil cylinder 11. It can be understood that the rod cavity and the rodless cavity of the hydraulic oil cylinder 11 are respectively connected with a balance valve, so that the whole hydraulic oil cylinder 11 can realize self-locking.
For the self-lock control module 132, it may include: the oil guide module, the servo valve and the two-position four-way electromagnetic directional valve. Wherein, the effect of leading the oil module is that supplementary oil circuit switches on, can have different implementation modes, only need including first oil inlet, second oil inlet and oil-out can, need two mouthful of oil intakes promptly and a mouthful oil outlet. The servo valve includes four oil ports (port P, port T, port a and port B), and the valve core thereof can realize switching between three positions (left position, right position and zero position). When the servo valve is at different positions, the conduction conditions of the four oil ports are correspondingly changed, for example, when the servo valve is at a left position, the oil port P is conducted with the oil port B; when the servo valve is in the right position, the oil port T is communicated with the oil port A; when the servo valve is in a zero position, the oil port T is communicated with the oil ports A and B. The two-position four-way electromagnetic directional valve comprises four oil ports (an oil port P, an oil port T, an oil port A and an oil port B), and a valve core of the two-position four-way electromagnetic directional valve can realize switching between two positions (a left position and a right position). When the two-position four-way electromagnetic reversing valve is in different positions, the conduction conditions of the four oil ports are correspondingly changed, for example, when the two-position four-way electromagnetic reversing valve is in a left position, the oil port P is conducted with the oil port B; when the two-position four-way electromagnetic directional valve is in the right position, the oil port T is communicated with the oil port A.
Furthermore, a first oil inlet of the oil guide module is connected with a second oil port of the first balance valve, and a second oil inlet of the oil guide module is connected with a second oil port of the second balance valve; and the oil outlet of the oil guide module is connected with the pilot oil ports of the first balance valve and the second balance valve. An oil port A of the servo valve is connected with a second oil port of the first balance valve, and an oil port B of the servo valve is connected with a second oil port of the second balance valve; and an oil port P of the servo valve is also connected with an oil outlet of the oil guide module. An oil port B of the two-position four-way electromagnetic directional valve is connected with an oil port P of the servo valve, and an oil port T of the two-position four-way electromagnetic directional valve is connected with an oil port T of the servo valve; the oil port P and the oil port T of the two-position four-way reversing valve are also connected with a hydraulic oil source 12.
In this embodiment, when the self-locking module 130 is composed of a balance valve, the self-locking control module 132 can realize the self-locking control function of the balance valve through the oil guiding module, the servo valve and the two-position four-way electromagnetic directional valve. In the self-locking control module 132, different oil circuit conduction states can be realized through different conduction states of the servo valve and the two-position four-way electromagnetic directional valve, so that the opening and closing of the balance valve can be effectively controlled, and the influence on the quick response characteristic of the system caused by frequent opening and closing of the balance valve is avoided.
Further, the oil guide module can have different embodiments, the first embodiment is that: lead oily module and include: a first check valve and a second check valve; an oil inlet of the first check valve is connected with a second oil port of the first balance valve, and an oil inlet of the second check valve is connected with a second oil port of the second balance valve; the oil outlet of the first one-way valve is connected with the oil outlet of the second one-way valve and used as the oil outlet of the oil guide module.
In the first embodiment, the check valve is a one-way valve, and hydraulic oil can only enter from the oil inlet and exit from the oil outlet. Therefore, the oil inlets of the two one-way valves are respectively used as the two oil inlets of the oil guide module, and the oil outlets of the two one-way valves are connected and then used as the oil outlets of the oil guide module, so that the oil guide function of the oil guide module is realized.
In this embodiment, the oil guiding module may include two check valves, oil inlets of the two check valves are oil inlets of the oil guiding module, and after the two oil outlets are connected, the two oil inlets are used as oil outlets of the oil guiding module, and may further guide oil for a pilot oil port of the balance valve, so as to effectively control opening and closing of the balance valve.
In a second embodiment of the oil guiding module, the oil guiding module is a shuttle valve, the shuttle valve has two oil inlets and an oil outlet, the two oil inlets of the shuttle valve are two oil inlets of the oil guiding module, the oil outlet of the shuttle valve is an oil outlet of the oil guiding module, and the oil outlet is connected with the pilot oil port of the balance valve, so as to guide oil for the pilot oil port of the balance valve, thereby effectively controlling the opening and closing of the balance valve.
Further, in connection with the implementation of each module of the hydraulic control valve group 13, as an alternative implementation for the hydraulic oil source 12, the hydraulic oil source 12 includes: the hydraulic system comprises an energy accumulator, an overflow valve, a third check valve, a hydraulic pump and an oil tank. The overflow valve can be used as a pressure control valve, and the overhigh pressure can be avoided. The energy accumulator can absorb impact vibration and limit pressure protection for the overflow valve. The one-way conduction characteristic of the one-way valve can also avoid the influence of overlarge return oil pressure on the system. The hydraulic pump is also used to adjust high pressure generated in various cases such as high pressure generated when the oil tank is supplied or high pressure generated when oil is returned.
And the oil tank is used for storing hydraulic oil.
Further, the energy accumulator is connected with an oil port P of the two-position four-way electromagnetic directional valve; one end of the overflow valve is connected with an oil port P of the two-position four-way electromagnetic reversing valve, and the other end of the overflow valve is connected with an oil port T of the two-position four-way electromagnetic reversing valve; an oil outlet of the third one-way valve is connected with an oil port P of the two-position four-way electromagnetic directional valve; the hydraulic pump is connected with an oil inlet of the third one-way valve; and the oil tank is connected with the hydraulic pump.
In the embodiment of the application, the hydraulic oil source consisting of the energy accumulator, the overflow valve, the one-way valve, the hydraulic pump and the oil tank can avoid generating overhigh pressure during oil supply, and further realize pressure maintaining and controlling of the system.
It will be appreciated that in the servo valve cylinder system 10, there may be more than one hydraulic ram 11, and thus, as an alternative embodiment, the servo valve cylinder system 10 comprises a plurality of hydraulic rams 11 and a plurality of hydraulic control valve banks 13; the number of the hydraulic oil cylinders 11 is the same as that of the hydraulic control valve groups 13; each hydraulic control valve group 13 is connected with one hydraulic oil cylinder 11, and the hydraulic control valve groups 13 connected with different hydraulic oil cylinders 11 are all connected with a hydraulic oil source 12.
In the embodiment of the application, when a plurality of hydraulic oil cylinders exist, a plurality of corresponding hydraulic control valve groups can be arranged, the self-locking module corresponding to each hydraulic oil cylinder is ensured to be controllable, the influence on the quick response characteristic of the system is avoided, and the working efficiency of the system is improved.
Further, as an alternative embodiment, the servo valve cylinder control system 10 includes a first hydraulic cylinder and a second hydraulic cylinder; the hydraulic control valve group 13 comprises a first hydraulic control valve group and a second hydraulic control valve group; the first hydraulic control valve group is respectively connected with the first hydraulic oil cylinder and the hydraulic oil source 12; the second hydraulic control valve group is connected to a second hydraulic cylinder and a hydraulic oil source 12, respectively.
In this application embodiment, when there are two hydraulic cylinder, correspond and set up two hydraulic control valves, improve the work efficiency of system.
In order to facilitate understanding of the technical solutions provided in the embodiments of the present application, the following describes an implementation principle of the servo valve cylinder system 10 with reference to a specific example.
Referring to fig. 2, an alternative implementation structure of a servo valve cylinder control system 10 according to an embodiment of the present disclosure is shown in fig. 2, where the structure includes two hydraulic cylinders 11 and two hydraulic control valve sets 13, and an oil guide module adopts a first implementation mode (including two check valves).
The system comprises the following components: the hydraulic pump comprises a two-position four-way electromagnetic reversing valve, a servo valve, a first one-way valve, a balance valve, an oil cylinder (namely a hydraulic oil cylinder 11), an energy accumulator, an overflow valve, a second one-way valve and a hydraulic pump. The oil tank is not shown in fig. 2, but the tank body below the hydraulic pump is the oil tank according to the connection relation.
Further, the balance valve (IV) comprises an oil port 1, an oil port 2 and an oil port 3. Here, the oil port 1 may be understood as a second oil port and the oil port 2 of the balance valve in the foregoing embodiment may be understood as a first oil port and the oil port 3 of the balance valve in the foregoing embodiment may be understood as a pilot oil port of the balance valve in the foregoing embodiment. The oil inlet of the first check valve is connected to the oil port 1 of the balance valve, and the other end of the first check valve is an oil outlet and is connected with the oil port 3 of the balance valve. The oil port P of the servo valve and the oil port P of the two-position four-way electromagnetic reversing valve are high-pressure (0-20Mpa), the oil port T is low-pressure, and the oil port A and the oil port B can be understood as an actuating mechanism (oil outlet or oil inlet)
Next, the flowing situation of hydraulic oil and the self-locking situation of the oil cylinder in the whole system under the condition that different oil paths of the two-position four-way electromagnetic directional valve I and the servo valve II are communicated are respectively introduced. In the following description of the embodiment, the two balancing valves and the two first check valves are both referred to, because the two balancing valves or the first check valve have the same operation principle, but the connected cylinder chambers are different. Wherein, the cylinder cavity comprises a rod cavity and a rodless cavity, the rod cavity is the cavity on the right side of the cylinder (fifthly) in the figure 2, and the rodless cavity is the cavity on the left side of the cylinder (fifthly) in the figure 2. Also, it should be understood that the operation principle is consistent for each group (two groups in total) of the structure including the cylinder(s), the hydraulic control valve group 13, and the hydraulic oil source 12 (sharing the same hydraulic oil source 12).
In the first situation, when the two-position four-way electromagnetic reversing valve is electrified to be in the left position, high-pressure oil is supplied to the oil port P of the servo valve from the oil port P of the two-position four-way electromagnetic reversing valve to reach the pilot oil port 3 of the balance valve to completely open the balance valve. Meanwhile, the first check valve is closed under the action of the high-pressure oil in the path, so that the high-pressure oil in the path cannot enter the oil port A, B of the servo valve II, namely the oil port 1 of the balance valve II, and further disorder on the oil path is caused to generate misoperation. And the oil port 1 and the oil port 2 of the balance valve are communicated, so that the oil path between the servo valve and the oil cylinder is completely smooth, the quick response characteristic of the servo valve cylinder control system 10 cannot be influenced due to the frequent opening and closing of the balance valve, and the positioning time is short and the positioning precision is high.
In the second situation, when the two-position four-way electromagnetic directional valve is powered off and positioned at the right position, on one hand, hydraulic oil of the pilot oil port 3 (and the oil port P of the servo valve) of the balance valve is directly returned to the oil port T through the oil port B of the two-position four-way electromagnetic directional valve for oil discharge, and on the other hand, hydraulic oil of the oil port 1 of the servo valve A, B and the balance valve is returned to the oil port T for oil discharge through the oil port B of the two-position four-way electromagnetic directional valve, so that the pilot oil port 3 and the oil port 1 of the balance valve are completely discharged, the balance valve is guaranteed to be effectively closed, and the self-locking of the oil cylinder is realized.
In the third situation, when the oil cylinder runs normally at a certain speed and is suddenly powered off, the two-position four-way electromagnetic directional valve is positioned at the right position due to power off (the servo valve is positioned near the zero position due to power off), the balance valve is closed because the hydraulic oil of the oil port 1 and the oil port 3 returns to the oil port T through the oil port B of the two-position four-way electromagnetic directional valve for oil discharge, the piston rod and the load of the oil cylinder continue to move forward under the action of inertia force, the hydraulic oil in the cavity (rod cavity or rodless cavity) in the advancing direction of the piston rod of the oil cylinder is compressed, so that high pressure is generated to prevent the piston rod and the load from continuing to move forward, when the pressure set by the side balance valve is exceeded, the hydraulic oil overflows (to protect the side cavity from generating excessive pressure), and returns to the oil tank through the first check valve and the two-position four-way electromagnetic directional valve until the piston rod and the load completely decelerate and stop, thereby avoiding excessive pressure and shock from the system.
The set pressure of the balance valve (iv) may be set with reference to a factory sample, or may be set according to a calculation result (or a test result) of the cylinder (v) operating at a certain speed and stopping at a certain distance.
In the fourth situation, when the oil cylinder runs normally at a certain speed, the servo valve suddenly returns to the zero position, the two-position four-way electromagnetic reversing valve keeps powered on the left position, the balance valve keeps on opening, an oil path between the servo valve and the oil cylinder keeps smooth continuously, a piston rod and a load of the oil cylinder continue to move forwards under the action of inertia force, hydraulic oil in a certain cavity of the oil cylinder is compressed to generate high pressure to prevent the piston rod and the load from continuing to move forwards, hydraulic oil leaks back to the oil tank through the servo valve on one way and flows to an oil port P through an oil port B of the first one-way valve and the two-position four-way electromagnetic reversing valve on the other way, the hydraulic oil is filled to an energy accumulator, and when the pressure exceeds the set pressure of the overflow valve. The energy accumulator can absorb impact vibration and has relief valve to avoid over high pressure and over great impact.
Furthermore, because the leakage amount of the servo valve II is large, when a certain actuating mechanism does not work in a self-locking mode, the two-position four-way electromagnetic reversing valve I is powered off to be positioned at the right position, the hydraulic oil supply of the actuating mechanism is cut off, the leakage amount of a hydraulic system can be reduced, the system can work more efficiently, and the effects of reducing heat, saving energy and reducing emission are achieved.
According to the technical scheme provided by the embodiment of the application, under the different conduction conditions of the two-position four-way electromagnetic reversing valve I and the servo valve II and the different operation conditions of the oil cylinder fifth, the oil cylinder fifth can be stably switched in a self-locking state or other states (such as oil unloading), and in the whole process, the system can quickly respond and the working efficiency of the system is improved; and the pressure in the whole system is protected and limited, and the safety of the system is higher.
In this document, relational terms such as first and second, and the like may be used solely to distinguish one entity or action from another entity or action without necessarily requiring or implying any actual such relationship or order between such entities or actions.
The above description is only an example of the present application and is not intended to limit the scope of the present application, and various modifications and changes may be made to the present application by those skilled in the art. Any modification, equivalent replacement, improvement and the like made within the spirit and principle of the present application shall be included in the protection scope of the present application.

Claims (7)

1. A hydraulic control valve assembly, comprising:
the self-locking module is connected with the hydraulic oil cylinder;
the self-locking control module is respectively connected with the hydraulic oil source and the self-locking module and is used for controlling the opening and closing of the self-locking module; when the self-locking module is opened, the hydraulic oil cylinder is in a self-locking state; when the self-locking module is closed, an oil way between the hydraulic oil cylinder and the hydraulic oil source is communicated;
the self-locking module comprises: a first counter-balance valve and a second counter-balance valve; the first oil port of the first balance valve is connected with the rodless cavity of the hydraulic oil cylinder, and the first oil port of the second balance valve is connected with the rod cavity of the hydraulic oil cylinder;
the self-locking control module comprises:
lead oily module, include: the oil inlet is connected with the oil inlet; the first oil inlet is connected with a second oil port of the first balance valve, and the second oil inlet is connected with a second oil port of the second balance valve; the oil outlet is connected with the pilot oil ports of the first balance valve and the second balance valve;
an oil port A of the servo valve is connected with a second oil port of the first balance valve, and an oil port B of the servo valve is connected with a second oil port of the second balance valve; an oil port P of the servo valve is also connected with an oil outlet of the oil guide module;
an oil port B of the two-position four-way electromagnetic reversing valve is connected with an oil port P of the servo valve, and an oil port T of the two-position four-way electromagnetic reversing valve is connected with an oil port T of the servo valve; the oil port P and the oil port T of the two-position four-way electromagnetic directional valve are also connected with the hydraulic oil source;
the oil guide module comprises:
a first check valve and a second check valve; an oil inlet of the first check valve is connected with a second oil port of the first balance valve, and an oil inlet of the second check valve is connected with a second oil port of the second balance valve; and the oil outlet of the first one-way valve is connected with the oil outlet of the second one-way valve and used as the oil outlet of the oil guide module.
2. The set of hydraulic control valves of claim 1, wherein the oil routing module is a shuttle valve.
3. The set of hydraulic control valves of claim 1, wherein the source of hydraulic oil comprises:
the energy accumulator is connected with the oil port P of the two-position four-way electromagnetic directional valve;
one end of the overflow valve is connected with an oil port P of the two-position four-way electromagnetic reversing valve, and the other end of the overflow valve is connected with an oil port T of the two-position four-way electromagnetic reversing valve;
an oil outlet of the third one-way valve is connected with an oil port P of the two-position four-way electromagnetic directional valve;
the hydraulic pump is connected with an oil inlet of the third one-way valve;
and the oil tank is connected with the hydraulic pump.
4. A servovalve cylinder system, comprising:
the hydraulic oil system comprises a hydraulic oil cylinder, a hydraulic oil source and a hydraulic control valve group;
wherein, the hydraulic control valve group includes:
the self-locking module is connected with the hydraulic oil cylinder;
the self-locking control module is respectively connected with the hydraulic oil source and the self-locking module and is used for controlling the opening and closing of the self-locking module; when the self-locking module is opened, the hydraulic oil cylinder is in a self-locking state; when the self-locking module is closed, an oil way between the hydraulic oil cylinder and the hydraulic oil source is communicated;
the self-locking module comprises: a first counter-balance valve and a second counter-balance valve; the first oil port of the first balance valve is connected with the rodless cavity of the hydraulic oil cylinder, and the first oil port of the second balance valve is connected with the rod cavity of the hydraulic oil cylinder;
the auto-lock control module includes:
lead oily module, include: the oil inlet is connected with the oil inlet; the first oil inlet is connected with a second oil port of the first balance valve, and the second oil inlet is connected with a second oil port of the second balance valve; the oil outlet is connected with the pilot oil ports of the first balance valve and the second balance valve;
an oil port A of the servo valve is connected with a second oil port of the first balance valve, and an oil port B of the servo valve is connected with a second oil port of the second balance valve; an oil port P of the servo valve is also connected with an oil outlet of the oil guide module;
an oil port B of the two-position four-way electromagnetic reversing valve is connected with an oil port P of the servo valve, and an oil port T of the two-position four-way electromagnetic reversing valve is connected with an oil port T of the servo valve; and an oil port P and an oil port T of the two-position four-way electromagnetic directional valve are also connected with the hydraulic oil source.
5. The servovalve cylinder system of claim 4, comprising a plurality of hydraulic rams and a plurality of sets of hydraulic control valves; the number of the hydraulic oil cylinders is the same as that of the hydraulic control valve groups; and each hydraulic control valve group is connected with one hydraulic oil cylinder, and the hydraulic control valve groups connected with different hydraulic oil cylinders are connected with the hydraulic oil source.
6. The servo valve cylinder system of claim 5, wherein the servo valve cylinder system comprises a first hydraulic cylinder and a second hydraulic cylinder; the hydraulic control valve group comprises a first hydraulic control valve group and a second hydraulic control valve group;
the first hydraulic control valve group is respectively connected with the first hydraulic oil cylinder and the hydraulic oil source; and the second hydraulic control valve group is respectively connected with the second hydraulic oil cylinder and the hydraulic oil source.
7. The servo valve cylinder control system of claim 4, wherein the hydraulic oil source comprises:
the energy accumulator is connected with an oil port P of the two-position four-way electromagnetic reversing valve;
one end of the overflow valve is connected with an oil port P of the two-position four-way electromagnetic reversing valve, and the other end of the overflow valve is connected with an oil port T of the two-position four-way electromagnetic reversing valve;
an oil outlet of the third one-way valve is connected with an oil port P of the two-position four-way electromagnetic directional valve;
the hydraulic pump is connected with the oil inlet of the third one-way valve;
and the oil tank is connected with the hydraulic pump.
CN202010262951.1A 2020-04-03 2020-04-03 Hydraulic control valve group and servo valve control cylinder system Active CN113494488B (en)

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CN114321049A (en) * 2021-12-27 2022-04-12 广东碧品居建筑工业化有限公司 Hydraulic oil cylinder control device and hydraulic system

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GB1421878A (en) * 1973-05-02 1976-01-21 Caterpillar Tractor Co Hydraulic system with selectively actuable shock absorbing means for a motor therein
CN103115028A (en) * 2013-03-12 2013-05-22 北京机械设备研究所 Electro-hydraulic servo actuator
CN104948538A (en) * 2015-06-03 2015-09-30 福建工程学院 Plate bending machine servo hydraulic system and construction method thereof
CN107013534A (en) * 2017-04-27 2017-08-04 机械科学研究院哈尔滨焊接研究所 Aero-engine key component inertia friction welder fluid power system
CN110131221A (en) * 2019-04-19 2019-08-16 武汉智仁传控技术有限公司 The hydraulic system of mechanical arm

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1421878A (en) * 1973-05-02 1976-01-21 Caterpillar Tractor Co Hydraulic system with selectively actuable shock absorbing means for a motor therein
CN103115028A (en) * 2013-03-12 2013-05-22 北京机械设备研究所 Electro-hydraulic servo actuator
CN104948538A (en) * 2015-06-03 2015-09-30 福建工程学院 Plate bending machine servo hydraulic system and construction method thereof
CN107013534A (en) * 2017-04-27 2017-08-04 机械科学研究院哈尔滨焊接研究所 Aero-engine key component inertia friction welder fluid power system
CN110131221A (en) * 2019-04-19 2019-08-16 武汉智仁传控技术有限公司 The hydraulic system of mechanical arm

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