A multifunctional electro-hydraulic flow control valve and a flow control method. The control valve comprises a main valve, a proportional pilot valve, a flow sensor, a multifunctional valve controller, a control cavity pressure sensor, an oil inlet pressure sensor, an oil outlet pressure sensor, a temperature sensor and a cloud storage. The invention has the characteristics that a flow of the main valve is continuously controlled without being influenced by load change without installing a pressure compensator in the system, and meanwhile, the valve has the function of a flow sensor, has low pressure loss and wide flow control range, and realizes integration of flow detection and control; and information such as flow, power and efficiency of each part in a hydraulic system is monitored in real time based on a multifunctional controller, key operation state monitoring, service life prediction and fault positioning of the control valve are achieved.

A multifunctional electro-hydraulic flow control valve and a flow control method. The control valve comprises a main valve, a proportional pilot valve, a flow sensor, a multifunctional valve controller, a control cavity pressure sensor, an oil inlet pressure sensor, an oil outlet pressure sensor, a temperature sensor and a cloud storage. The invention has the characteristics that a flow of the main valve is continuously controlled without being influenced by load change without installing a pressure compensator in the system, and meanwhile, the valve has the function of a flow sensor, has low pressure loss and wide flow control range, and realizes integration of flow detection and control; and information such as flow, power and efficiency of each part in a hydraulic system is monitored in real time based on a multifunctional controller, key operation state monitoring, service life prediction and fault positioning of the control valve are achieved.

A solenoid valve (100) comprising a solenoid assembly (104) and a dual valve assembly (102) for fluid flow control and pressure relief. The dual valve assembly (102) comprising a valve body (300), upper stopper ring (113) and a lower stopper ring (307). A flow arrangement (200) comprising, a primary moving assembly (240) and a secondary moving assembly (213) is disposed inside the valve body (300). The primary moving assembly (240) having a primary mover (230) and an O-ring holder (208). The secondary moving assembly (213) comprising a sliding member (215), a supporting ring (214), a pressure-relief spring (211) and a pressure-adjusting mechanism (205). The flow arrangement (200) moves up when a solenoid coil (103) is energized resulting in normal fluid flow, the secondary moving assembly (213) moves down under excessive fluid pressure with the solenoid coil (103) de-energized. A reverse fluid flow is facilitated under excessive fluid pressure.

A hydraulic component includes a piston and a cylinder with a piston receiving space in which the piston is displaceably arranged while defining a chamber, via which a pressure may be applied to a first end face of the piston, from a control chamber, via which pressure may be applied to a second end face of the piston which faces away from the first end face. A first hydraulic line and a second hydraulic line open into the chamber and a control line, which branches off from the first hydraulic line, opens into the control chamber. Due to the respective pressure ratio between the pressure in the chamber and the control chamber, the piston is displaceable from a closed position, in which the first and second hydraulic lines are fluidly decoupled, into an open position, in which the first and second hydraulic lines are fluidly connected, and vice versa.

Embodiments of a directional valve assembly that provides a single device with functionality of a two-position design for automated operation and functionality of a three-position design for manual operation. The embodiments can include a housing with a piston chamber and a spool member that transits in the housing to regulate the flow of a working fluid to a cylinder. The embodiments can also have one or more pilot operators that regulate the flow of pilot air into the piston chamber to move the spool member between two positions, i.e., two open positions. The embodiments can also have a manual operator (e.g., a lever) that can move the spool to the open positions and to a closed position. In one embodiment, the spool member is configured to remain in either a first position, a second position, or a third position in the absence of an outside stimulus on the pilot operators.

An electropneumatic valve assembly comprises an electropneumatic pilot stage and a pneumatic power stage which is actuated by the pilot stage. Each pilot valve switches at least two power valves, and the valve assembly has a housing with an electrical signal input, with a compressed-air port, at least one vent port and at least one working outlet. The housing is layered with a pilot stage housing and a power stage housing connected along a substantially planar parting surface. At least one sealing element is between the pilot stage housing and power stage housing surrounding a control pressure region between the pilot stage housing and power stage housing. The control pressure region has two actuation regions for two power valves and has a duct-like connection with a defined flow cross section between the two actuation regions. An outlet of the associated pilot valve opens into the control pressure region.

A valve arrangement for hydraulic control of a piston-cylinder of a power switch (7) contains a main stage having a first main valve (31) and a second main valve (32), and a pilot stage having at least one pilot valve (3, 4). In order to permit the first main valve (31) to remain securely in the opened state, even in the event of pressure oscillations, the main valve has a total of four control surfaces, of which a second (F5) and a third (F6) control surface operate in a closing manner and a fourth control surface (F7) operates in an opening manner. For this purpose, the second control surface (F5) is connected to the high-pressure line (P), the third control surface (F6) is connected to the low-pressure line (T), and the fourth control surface (F7) is connected to the output-side valve connection (35) of the first main valve (31). The size ratio of the opening control surfaces (F4, F7) to the closing control surfaces (F5, F6) is selected such that in the open condition of the first main valve (31) an opening resulting force is maintained.

A proportional valve is provided having a pilot control valve that can be controlled by means of a control signal and having a booster valve that can be actuated by means of the pilot control valve. The proportional valve has a compressed-air connection for connecting a compressed-air supply, a working connection, and an air-removal connection. The booster valve has three valve elements, which are arranged one after the other and can each be moved in an axial direction against a spring force.

A valve arrangement has two main valves which are each preloaded by a spring device into a first switching position, and which can each be switched into a second switching position by means of an assigned pilot valve. The pilot medium required for switching is provided with a pilot pressure at a pilot connection of each pilot valve. The main valves are each equipped with a working valve section each of which are fluidically connected to one another. In addition, each main valve contains a monitoring valve section. The monitoring valve sections are designed to provide the venting of at least one pilot connection when the two main valves are in different switching positions. This allows a fluid-actuated actuator to be controlled in accordance with high safety standards.

A hydraulic valve with electropneumatic activation includes an air inlet that receives pressurized air from an air compressor and directs it into a line of the cylinder. The line is connected to an extension line attached to a solenoid extension valve that allows or blocks the passage of pressurized air from the extension line to a rear line. The rear line is attached to the rear chamber of the cylinder and connected to a retraction line attached to a solenoid retraction valve that allows or blocks the passage of pressurized air from the retraction line to an anterior line, which is attached to the front chamber of the cylinder. Thus, the passage of pressurized air is managed according to the desired movement of the stem of the hydraulic actuator. The pneumatic tubes are eliminated and electropneumatic valves are replaced by solenoid valves incorporated into the cylinder of the hydraulic valve.