CN211692994U

CN211692994U - Hydraulic reversing valve control switching combination valve

Info

Publication number: CN211692994U
Application number: CN201922231796.2U
Authority: CN
Inventors: 王力; 袁洪回; 郭智; 郑红
Original assignee: SICHUAN LINGFENG AVIATION HYDRAULIC MACHINERY CO Ltd
Current assignee: SICHUAN LINGFENG AVIATION HYDRAULIC MACHINERY CO Ltd
Priority date: 2019-12-12
Filing date: 2019-12-12
Publication date: 2020-10-16
Anticipated expiration: 2029-12-12

Abstract

The utility model discloses a hydraulic pressure switching-over valve accuse switching combination valve, aim at in order to solve that actuating element need have different velocities of movement in an orientation, another orientation keeps a velocity of movement's problem. The utility model discloses a following technical scheme realizes: the two-position four-way electromagnetic reversing valve is communicated with a two-position three-way electromagnetic reversing valve connected with the far end by a two-way hydraulic pipeline by utilizing a through-flow window communicated with the oil inlet P and the oil return port R, and the two-position four-way electromagnetic reversing valve is communicated with a first damping element and an actuating element to form an oil loop by utilizing a second damping element communicated with a state switching valve and a hydraulic pipeline communicated with the oil return port R and the actuating element respectively; the annular valve controls the two-position three-way electromagnetic directional valve 3 to be powered on or powered off through the two-position four-way electromagnetic directional valve, controls the working position of the state conversion valve, quickly selects and changes the movement direction and the movement speed of the actuating element, and realizes the movement speed switching of the flow direction and the flow rate of the oil liquid of the actuating element.

Description

Hydraulic reversing valve control switching combination valve

Technical Field

The utility model relates to a mainly used control two effect executive component speed switching hydraulic control system. The actuator has the same speed of movement in one direction and two or more speeds of movement in the opposite direction.

Background

In a hydraulic system, an actuator refers to an element that converts pressure energy of a fluid into mechanical energy. The hydraulic motor can complete the required work of the machine, such as 'force' and 'speed' (the hydraulic cylinder is an executive component which can change pressure energy into reciprocating linear motion and output force and speed), such as 'torque' and 'rotating speed', and the hydraulic motor inputs hydraulic oil and converts the hydraulic oil into the executive component which can continuously rotate and output the torque and the rotating speed. The power element converts the mechanical energy of the prime mover into the pressure energy of the fluid, and the oil pump actuators in the hydraulic system, such as hydraulic cylinders and hydraulic motors, raise, lower, advance, retreat, rotate, and perform various actions. The hydraulic oil pump provides hydraulic power, and hydraulic oil is controlled by the hydraulic valve to enter the hydraulic oil cylinder to realize the reciprocating motion of the hydraulic oil cylinder. In modern hydraulic systems, different speeds of movement of the actuator are often required under different operating conditions in order to achieve various functions of the hydraulic system. The speed regulation and the movement direction change of the actuating element of the hydraulic system are realized by a control valve. Since the pressure depends on the load and the speed depends on the flow, slowing is a reduction in the flow to the actuator, and if the pump wears out severely, the volumetric efficiency decreases, the leakage is large and the output flow is small. If the flow valve is abnormal, the oil flows back to the oil tank from the overflow valve, resulting in a smaller flow rate to the actuator. If the control valve is abraded and seriously abraded, the gap is larger, the valve core has larger leakage, when the self sealing of the executing element is not good, oil liquid has leakage, and the sealing ring has impurities to influence the work of the valve. The flow control valve controls the movement of the actuator by adjusting the flow rate of the valve port by changing the flow area of the valve port, and the hydraulic control valve is a pressure control valve capable of changing the movement speed of the actuator. The phenomenon of equipment halt caused by the fault of the hydraulic cylinder is rare, and when a valve core of a flow valve or a directional valve is clamped or a valve hole is blocked, the hydraulic cylinder is easy to malfunction or malfunction. The piston rod and the cylinder barrel are stuck or the hydraulic cylinder is blocked, and at the moment, the hydraulic cylinder does not act or acts slightly no matter how the hydraulic cylinder is operated. When the control pressure of the hydraulic system is too low, the throttling resistance in the control pipeline is possibly too large, the flow valve is improperly adjusted, the control pressure is improper, and the pressure source is interfered. Under the condition of low temperature, the hydraulic oil has high viscosity and poor fluidity, so that the hydraulic cylinder acts slowly. The servo control system mainly shows inaccurate piston rod position, insufficient thrust, speed reduction, unstable work and the like, and the reasons are internal leakage of the hydraulic cylinder. The internal leakage of the hydraulic cylinder comprises leakage caused by excessive abrasion of a hydraulic cylinder body seal, a piston rod and seal cover seal, a piston seal and the like. The deformation, abrasion or form and position tolerance of parts in the hydraulic cylinder are out of limit, and the action resistance is overlarge, so that the piston speed of the hydraulic cylinder is changed along with the difference of stroke positions, slippage or crawling occurs, the resistance is increased, and the speed is reduced. The loop for controlling the movement speed of the actuating element by controlling the flow of the medium is divided into a speed regulating loop and a direction control loop according to different functions. The governor circuit is used to control the speed of movement of the individual actuators and may use a throttle or governor valve to control the flow rate, the throttle valve controlling the flow rate of the hydraulic pump into the cylinder (the excess flow rate returning to the tank through the spill valve) and thereby controlling the speed of movement of the cylinder, a form known as throttle governor. In the governor circuit, as the load increases, the hydraulic pump and the hydraulic motor leak, and thus the speed changes. In the throttling speed regulating loop, a large amount of oil overflows from an overflow valve and returns to an oil tank, which is the main reason of large energy loss, high temperature rise and low efficiency. The pressure regulating loop regulates and limits the highest working pressure and working pressure of the hydraulic system, or the executing mechanism realizes multi-stage pressure conversion at different stages of the working process. And multi-stage pressure transformation is realized in different stages. Relief valves are commonly used to accomplish this function. Relief valves are commonly used to accomplish this function. The directional control circuit is a circuit that controls the flow direction of the hydraulic medium. The loop which controls the moving direction of a single actuating element by using a directional control valve to enable the single actuating element to move in the positive direction and the negative direction or stop is called a reversing loop. A circuit for preventing the actuator from moving due to leakage caused by external factors such as load when the actuator is stopped is called a lock circuit. The hydraulic cylinder is an actuator for realizing linear reciprocating motion and is an element for converting pressure energy of fluid into mechanical energy. The driving mechanism makes linear reciprocating motion, the input is pressure and flow, and the output is force and speed. The movement in one direction is realized by hydraulic acting force, and the movement in the other direction is realized by spring force, gravity and the like; the movement of the double-acting hydraulic cylinder in two directions is realized by hydraulic acting force; but the volume and the weight are large, the torque pulsation is generated, and the low-speed stability is poor. In practical application, the hydraulic system usually changes the oil circuit connection of the single-rod cylinder through a control valve, so that the hydraulic system has different working modes, and the working cycle of fast forward (differential connection oil inlet) is obtained. When the hydraulic cylinder is under high speed and heavy load, the speed is greatly influenced by the load change, namely, when the hydraulic cylinder of the loop is under high speed and heavy load, the speed is greatly influenced by the load change, and the speed rigidity is poor; the oil inlet throttling speed regulation loop has both overflow loss and throttling loss, and the loop efficiency is lower; the speed is greatly influenced by load change, and the loop has different maximum bearing capacity under different throttle valve flow areas. The speed control range of the circuit is limited. In the throttle control circuit, when the load changes, the flow rate passing through the throttle valve changes due to the change in the pressure difference between the front and rear of the throttle valve, so that the speed load characteristic of the circuit is poor due to the change in the flow rate returning through the throttle valve. The speed load characteristic of the road is poor. The pressure of an oil return cavity of the oil return throttling speed regulating loop is high, particularly when the load is close to zero, the pressure is high, the pressure of the oil return cavity of the oil return throttling speed regulating loop is high, particularly when the load is close to zero, the pressure is high, the safety, the sealing and the service life of an oil return pipe are influenced, and the safety, the sealing and the service life of the oil return pipe are influenced. In a differential circuit, the valves and pipes through which the flow of the pump and the flow of the rod chambers of the cylinders flow together should be dimensioned for the resultant flow, which would otherwise result in excessive pressure losses, and the valves and pipes should be dimensioned for the resultant flow, which would otherwise result in excessive pressure losses and excessive supply pressure when the pump is unloaded. Usually a speed change-over circuit is used to change over the speed of the actuator. The switching process is required to be stable, and the switching precision is high. According to the difference of the speed before and after switching, there is the switching of fast-working speed or two working speeds. The switching circuit of the rapid movement and the work feeding uses the right position work of the stroke valve of the speed switching circuit switching valve, the piston of the hydraulic cylinder rapidly advances to a preset position, sometimes the pipeline needs to be connected very long, and the pressure loss is large. At the instant of the speed change, a sudden advance of the feed member is caused. The loop in which the actuator starts, stops or changes direction of motion is now referred to as the directional control loop. Common directional control loops are: a reversing loop, a locking loop and a braking loop. The reversing loop adopts a two-position four-way reversing valve and a three-position four-way reversing valve to reverse the double-acting hydraulic cylinder. The two-position valve only can make the executive component move forward and backward, the three-position valve has a middle position function, the middle position function can realize automatic reciprocating motion by a spring or a single-action hydraulic cylinder returned by gravity, but the piston can not keep a stop position for a long time due to leakage of a sliding valve of the middle position function, so that the locking precision is not high. On the occasions with larger flow and higher requirements on the reversing stability, a reversing loop of the electromagnetic reversing valve cannot adapt, and a manual reversing valve or a motor-driven reversing valve is often used as a pilot valve or a reversing loop of an electro-hydraulic reversing valve is used for frequent continuous reciprocating motion. The reversing loop adopting the mechanical-hydraulic reversing valve is mainly used in occasions with high movement speed of working parts and low requirement on reversing precision. Malfunction is caused by pressure shock or fluctuation in the pipe. The loop is suitable for the situation that the number of the actuators is not large, and the load is not changed greatly. When one oil source supplies oil to a plurality of actuators, each actuator is operationally restricted by the mutual influence of pressure and flow rate in the circuit.

The reversing valve is used as an important direction control valve, the change executing element pushes the valve core to overcome various resistances to move relatively in the valve body by external force to change the direction of liquid flow in an oil path of the executing element so as to operate the hydraulic cylinder to reverse, and the direction control of the moving part change executing element is realized. If the motion resistance is too large or the driving force is too small, the valve core of the actuating element is changed to be difficult to reverse and even to cause wrong reversing. The reason that the motion resistance is too large to change the execution element or the driving force is too small is many, the reversing valve cannot reverse due to too large hydraulic force, the valve core can generate hydraulic force when liquid flows through the reversing valve, the hydraulic force of the execution element is changed to comprise transient hydraulic force and steady-state hydraulic force, and the steady-state hydraulic force is force acted on the valve core due to momentum change when the valve changes a certain opening degree of the execution element and the liquid flow is stable. The transient hydrodynamic force is the force of liquid flow in the valve cavity acting on the valve core due to acceleration or deceleration in the process of changing the opening of the valve port. Under the conditions that the external load of a hydraulic change execution element pressure system is large, the inertia is large, the degree change is large, and the requirement for changing the speed of the execution element by reversing precision is high, the hydraulic force is mainly transient hydraulic force when a reversing valve is selected, otherwise, hydraulic impact and reversing failure can be caused. The transient hydraulic power is large, the valve core cannot be driven to move by changing the electromagnetic thrust of the electromagnetic reversing valve of the actuating element, and the hydraulic power is larger than the electromagnetic thrust, so that the reversing is failed. On the other hand, if the flow discharged from the accumulator is large, the actuator is changed to exceed the rated flow of the electromagnetic directional valve, the hydrodynamic force is larger than the electromagnetic force, and the direction change is not easy. When the system oil return pipeline is associated with the pipeline for controlling the change actuator by the hydraulic change valve, if the oil return back pressure is high, the change valve of the hydraulic change actuator can not change direction very possibly. In practice, the return oil is always back-pressured, and the back pressure is higher when the flow rate is larger. When the back pressure exceeds the elastic force of the return spring changing actuator, the actuator is changed, and the hydraulic reversing valve cannot reverse.

SUMMERY OF THE UTILITY MODEL

The utility model aims at the weak point that prior art exists, provide an efficient, speed switching process is steady, and the change over point position is accurate, need have different velocities of motion in a double action executive component orientation, and another orientation keeps the double action executive component velocity switching hydraulic control valve of another kind of velocity of motion. The problem that the actuator needs to have different movement speeds in one direction and maintain one movement speed in the other direction is solved.

The utility model provides a technical scheme that its technical problem adopted is: a hydraulic reversing valve control switching combination valve comprises: through the ring valve 1 of hydraulic pressure pipeline two-way intercommunication execute component 7, its characterized in that: the annular valve 1 is communicated with a two-position four-way electromagnetic reversing valve 2 and a two-position three-way electromagnetic reversing valve 3 connected with a far end through a two-way hydraulic pipeline by utilizing a through-flow window communicated with an oil inlet P and an oil return port R, and the two-position four-way electromagnetic reversing valve 2 is respectively communicated with a state switching valve 4 and a second damping element 6 which is communicated with an execution element 7 and is connected to the oil return port R through the two-way hydraulic pipeline; the state change valve 4 is respectively communicated with the first damping element 5 and the actuating element 7 through a two-way hydraulic pipeline to form an oil liquid loop; the annular valve 1 is communicated with the oil inlet P and the oil return R, the two-position four-way electromagnetic directional valve 2 is used for controlling the two-position three-way electromagnetic directional valve 3 to be powered on or powered off, the working position of the state conversion valve 4 is controlled, the movement direction and the movement speed of the actuating element 7 are rapidly selected and changed, and the movement speed switching of the oil flow direction and the oil flow of the actuating element 7 is realized.

The utility model discloses compare and have following beneficial effect in prior art:

the efficiency is high. The two-position four-way electromagnetic directional valve 2 is respectively communicated with a state conversion valve 4 and a second damping element 6 which is connected to an oil return port R hydraulic pipeline and communicated with an actuating element 7 by a two-way hydraulic pipeline; the first damping element 5 and the actuating element 7 are respectively communicated through the two-way hydraulic pipeline of the state conversion valve 4 to form an oil liquid loop, so that the overflow loss of the hydraulic control valve is small, and the efficiency is high. The defects that the speed of the hydraulic cylinder is greatly influenced by load change and the speed rigidity is poor when the hydraulic cylinder is at high speed and under heavy load are overcome; the overflow loss of the oil-taking throttling speed-regulating loop is large, the loop efficiency is low, and the speed is greatly influenced by the load change.

The degree switching process is stable. The utility model discloses utilize the logical, outage control state change-over valve 4's of two-position four-way solenoid directional valve 2 work position, the size of the 7 outflow of control executive component, through the logical, outage of control solenoid directional valve, the fast speed switch stationarity is good, and the transposition point position is accurate, and speed stability is good than the volume speed governing return circuit.

The utility model discloses a two-position three-way solenoid directional valve 3's the fluid flow direction of logical, outage control state execute component 7. The principle scheme of the hydraulic control valve is that one-way damping valves are respectively arranged at an oil inlet part and an oil return part of an execution element, and the size of oil flow flowing out of the execution element is changed to realize that the execution element moves at different speeds in one direction and keep the other moving speed in the other direction. The problem that the actuating element needs to have different movement speeds in one direction and maintain one movement speed in the other direction is solved.

Drawings

Fig. 1 is the principle schematic diagram of the hydraulic reversing valve control switching combination valve of the utility model.

In the figure: the system comprises a 1-ring through valve, a 2-three-position four-way reversing valve, a 3-two-position three-way electromagnetic reversing valve, a 4-state switching valve, a 5-first damping element, a 6-second damping element and a 7-actuating element.

The present invention is further described with reference to the following figures and examples, but the invention is not limited thereby within the scope of the described embodiments. All of these concepts should be considered within the scope of the present disclosure.

Detailed Description

See fig. 1. In a preferred embodiment described below, a dual acting actuator speed-switching hydraulic control system includes: the annular valve 1 of the actuating element 7 is in bidirectional communication via a hydraulic line. The annular valve 1 is communicated with a two-position four-way electromagnetic reversing valve 2 and a two-position three-way electromagnetic reversing valve 3 connected with a far end through a two-way hydraulic pipeline by utilizing a through-flow window communicated with an oil inlet P and an oil return port R, and the two-position four-way electromagnetic reversing valve 2 is respectively communicated with a state switching valve 4 and a second damping element 6 which is communicated with an execution element 7 and is connected to the oil return port R through the two-way hydraulic pipeline; the state change valve 4 is respectively communicated with the first damping element 5 and the actuating element 7 through a two-way hydraulic pipeline to form an oil liquid loop; the annular valve 1 is communicated with the oil inlet P and the oil return R, the two-position four-way electromagnetic directional valve 2 is used for controlling the two-position three-way electromagnetic directional valve 3 to be powered on or powered off, the working position of the state conversion valve 4 is controlled, the movement direction and the movement speed of the actuating element 7 are rapidly selected and changed, and the movement speed switching of the oil flow direction and the oil flow of the actuating element 7 is realized.

The two-position four-way electromagnetic directional valve 2 controls the working position of the state conversion valve 4. The right end of the state conversion valve 4 is communicated with an oil return port R, the left end of the state conversion valve 4 is controlled to work by the power-on and power-off of the two-position three-way electromagnetic reversing valve 3, when the two-position three-way electromagnetic reversing valve 3 is powered on, the two-position three-way electromagnetic reversing valve 3 works at the right position, an oil inlet P is communicated with the two-position three-way electromagnetic reversing valve 3 through a through-flow window of the annular valve 1, pressure oil is communicated to the left end of the state conversion valve 4 through the right position of the two-position three-way electromagnetic reversing valve 3, and the hydraulic pressure at the left end of the state conversion valve 4 overcomes the spring force at the; when the two-position three-way electromagnetic directional valve 3 is powered off, the two-position three-way electromagnetic directional valve 3 works at the left position, the oil inlet P is communicated with the left position of the two-position three-way electromagnetic directional valve 3 through the through-flow window of the annular valve 1, and at the moment, the pressure oil is sealed by the left position of the two-position three-way electromagnetic directional valve 3. The oil return port R is connected to the left position of the two-position three-way electromagnetic directional valve 3 through the through-flow window of the annular valve 1 and is connected to the left end of the state switching valve 4, and the hydraulic pressure at the left end of the state switching valve 4 cannot overcome the spring force at the right end thereof, so that the state switching valve 4 works at the right position.

The two-position four-way electromagnetic directional valve 2 and the two-position three-way electromagnetic directional valve 3 are connected with an oil return port R hydraulic pipe and are connected in parallel in a hydraulic oil circuit, the two-position three-way electromagnetic directional valve 3 controls the on and off of the two-position four-way electromagnetic directional valve 2 communicated with an oil inlet P, the station state of the state change switching valve 4 is switched, the motion direction of the execution element 7 is changed, the state change switching valve 4 controls the oil flowing out of the left cavity of the execution element 7 to generate damping or not to generate damping and the flow of the oil flowing out of the left cavity through a first damping element 5 connected with the left cavity of the execution element 7, and the motion speed switching of the execution element 7 is.

The two-position four-way electromagnetic directional valve 2 is connected with a second damping element 6 through a hydraulic pipeline which is connected between an oil return port R of the annular valve 1 and the actuating element 7 in a bypassing mode, and the second damping element 6 is used for generating damping for oil entering or flowing out of a right cavity of the actuating element 7.

When the pressure of an oil inlet P of the annular valve 1 is zero, the annular valve 1 is communicated with an annular valve 1 of an actuating element 7 in a two-way mode through a hydraulic pipeline, when the pressure P of the oil inlet is rated oil supply pressure, the right end of the annular valve 1 is communicated with the oil inlet P, the annular valve 1 works on the right actuating element 7 to move to the left end quickly and move to the right end slowly under the action of left end spring force and pressure oil P, fluid from a pressure source enables the hydraulic pipeline of the oil inlet P to be communicated with a two-position three-way electromagnetic directional valve 3 through an oil passing window of a valve core of the annular valve 1, the two-position three-way electromagnetic directional valve 3 is powered off all the time, at the moment, the electromagnetic directional valve 3 works in the left position, and; and meanwhile, the two-position four-way electromagnetic reversing valve 2 is powered off, the electromagnetic reversing valve 2 works in a left-position function, the two-position four-way electromagnetic reversing valve 2 connected with the two-position three-way electromagnetic reversing valve 3 in parallel is connected with the two-position three-way state switching valve 4 through a through-flow window of a valve core of the two-position four-way electromagnetic reversing valve, a hydraulic pipeline of an oil inlet P is connected with the two-position three-way state switching valve 4, two ends of the two-position three-way state switching valve 4 are both communicated with an. The oil inlet P is communicated with a left cavity of the actuating element 7 through the two-position four-way electromagnetic reversing valve 2 and the state switching valve 4, the actuating element 7 moves rightwards under the action of pressure oil, 2 oil paths of oil in a right cavity of the actuating element 7 can return to the oil return port R, one oil path is communicated with the annular valve 1, and the oil path is not communicated because the annular valve 1 works at the right position; therefore, the oil in the right cavity of the actuator 7 can only be connected to the oil return port R through the second damping element 6 and the two-position four-way electromagnetic directional valve 2. In this circuit, there is no throttling when the pressure oil enters the actuator 7, and the pressure oil passes through the second one-way damping valve when flowing out of the actuator 7, throttling occurs, and the actuator 7 moves to the right end at a slow speed. When the actuating element 7 moves towards the left end, the two-position three-way electromagnetic reversing valve 3 is powered off all the time, the two-position four-way electromagnetic reversing valve 2 is powered on all the time, and at the moment, the two-position four-way electromagnetic reversing valve 2 works at the right position; the oil inlet P is communicated with the right position of the two-position four-way electromagnetic reversing valve 2, pressure oil flows through a valve core through-flow window at the right position of the two-position four-way electromagnetic reversing valve 2 to enter a second damping element 6 and then enters a right cavity of an actuating element 7, 2 oil paths are arranged when the oil in the right cavity of the actuating element 7 reaches the state switching valve 4, one path directly reaches through a pipeline, and the other path reaches through a one-way damping valve. Because the state change-over valve 4 works at the right position, oil in the left cavity of the actuating element 7 can only enter the right position of the state change-over valve 4 through a pipeline, the oil flows through a through-flow window of a right valve core of the state change-over valve 4 to enter the right position of the two-position four-way electromagnetic directional valve 2, and the oil flows to an oil return port R through a pipeline. In this circuit, there is no throttling when the pressure oil enters the right cavity of the actuator 7, there is no throttling when the pressure oil exits the actuator 7, and the actuator 7 moves rapidly to the left.

Embodiment with slow movement of the actuator 7 to the left and right end: the two-position three-way electromagnetic directional valve 3 is always electrified, the electromagnetic directional valve 3 works at the right position, and the oil inlet P is communicated with the electromagnetic directional valve 3; the oil inlet P is connected with the left end of the state conversion valve 4 through a valve core through-flow window of the electromagnetic directional valve 3, the right end of the state conversion valve 4 is communicated with the oil return port R, and the hydraulic pressure at the left end of the state conversion valve 4 overcomes the spring force at the right end to enable the state conversion valve 4 to work at a left position; meanwhile, the two-position four-way electromagnetic directional valve 2 is powered off, and the electromagnetic directional valve 2 works in a left position at the moment. The flow path of the pressure oil is as follows: the pressure oil enters the oil inlet P, passes through a through-flow window of the valve core of the right-position function of the annular valve, and simultaneously enters the two-position four-way electromagnetic directional valve 2 and the two-position three-way electromagnetic directional valve 3, and the electromagnetic directional valves 2 and 3 are connected in parallel.

The pressure oil enters the left position of the state conversion valve 4 through a through flow window of a left valve core of the two-position four-way electromagnetic directional valve 2, the pressure oil enters the first damping element 5 through a through flow window of the left valve core of the state conversion valve 4, and the pressure oil enters the left cavity of the actuating element 7 through a through flow window of the first damping element 5. Oil in the right cavity of the actuating element 7 enters the left position of the two-position four-way electromagnetic reversing valve 2 through a through-flow window of the second damping element 6, and pressure oil flows to the oil return port R through a through-flow window of a left valve core of the two-position four-way electromagnetic reversing valve 2. In this oil return path, the oil entering the right chamber of the actuator 7 is damped by the first damping element 5, and the oil in the right chamber of the actuator 7 is throttled by the second damping element 6 when flowing out, so that the actuator 7 moves to the right at a slow speed. And then the two-position four-way electromagnetic directional valve 2 is electrified, and the electromagnetic directional valve 2 works at the right position. The flow path of the pressure oil is as follows: the pressure oil enters the oil inlet P, passes through a through-flow window of the valve core of the right-position function of the annular valve, and simultaneously enters the two-position four-way electromagnetic directional valve 2 and the two-position three-way electromagnetic directional valve 3, and the electromagnetic directional valves 2 and 3 are connected in parallel. The pressure oil enters the second damping element 6 through the through-flow window of the right valve core of the two-position four-way electromagnetic directional valve 2 and enters the right cavity of the actuating element 7 through the through-flow window of the second damping element 6. The oil in the left cavity of the actuating element 7 reaches the state switching valve 4, and 2 oil paths are arranged, wherein one oil path directly reaches the state switching valve through a pipeline, and the other oil path directly reaches the state switching valve through a one-way damping valve. Because the state change valve 4 works at the left position, oil in the left cavity of the actuating element 7 can only enter the left position of the state change valve 4 through the through-flow window of the first damping element 5, the oil flows into the right position of the two-position four-way electromagnetic directional valve 2 through the through-flow window of the left valve core of the state change valve 4, and the oil flows to the oil return port R through a pipeline. In the oil return path, oil entering the right chamber of the actuator 7 is undamped, and when oil in the left chamber of the actuator 7 flows out, throttling occurs through the first damping element 5, so that the actuator 7 moves to the left end slowly.

When the system is not supplying pressure, the circulation valve 1 always works in the left position under the action of the spring force thereof. At this time, the left and right chambers of the actuator 7 are communicated with each other through the annular valve and communicated with the system oil return fluid.

The foregoing is directed to the preferred embodiment of the present invention, and it is noted that the above-mentioned embodiments illustrate rather than limit the invention, and that those skilled in the art will be able to design alternative embodiments without departing from the scope of the appended claims. It will be apparent to those skilled in the art that various modifications and improvements can be made without departing from the spirit and substance of the invention, and these modifications and improvements are also considered to be within the scope of the invention.

Claims

1. A hydraulic reversing valve control switching combination valve comprises: through the ring valve (1) of hydraulic pressure pipeline two-way intercommunication execute component (7), its characterized in that: the two-position four-way electromagnetic reversing valve (2) and the two-position three-way electromagnetic reversing valve (3) connected with the far end are communicated through a two-way hydraulic pipeline by the aid of the circulating valve (1) communicated with the oil inlet P and the oil return port R, and the two-position four-way electromagnetic reversing valve (2) is respectively communicated with the state switching valve (4) and a second damping element (6) communicated with the execution element (7) and connected to the oil return port R through a two-way hydraulic pipeline; the state conversion valve (4) is respectively communicated with the first damping element (5) and the actuating element (7) through a bidirectional hydraulic pipeline to form an oil liquid loop; the annular valve (1) is communicated with the oil inlet P and the oil return R, the two-position four-way electromagnetic directional valve (2) is used for controlling the power-on or power-off of the two-position three-way electromagnetic directional valve (3), the working position of the state switching valve (4) is controlled, the movement direction and the movement speed of the execution element (7) are rapidly selected and changed, and the movement speed switching of the oil flow direction and the oil flow of the execution element (7) is realized.

2. The hydraulic reversing valve-controlled switching combination valve of claim 1, wherein: the right end of the state conversion valve (4) is communicated with an oil return port R, the left end controls the working position of the state conversion valve (4) through the connection and disconnection of a communicated two-position three-way electromagnetic directional valve (3), the two-position three-way electromagnetic directional valve (3) is connected, the two-position three-way electromagnetic directional valve (3) works at the right position, an oil inlet is communicated with the two-position three-way electromagnetic directional valve (3) through a through flow window of a circulating valve (1), pressure oil P is communicated to the left end of the state conversion valve (4) through the right position of the two-position three-way electromagnetic directional valve (3), and the hydraulic pressure at the left end of the state conversion valve (4) overcomes the spring force at the right end of the state conversion valve (.

3. The hydraulic reversing valve-controlled switching combination valve of claim 1, wherein: the two-position three-way electromagnetic directional valve (3) is powered off, the two-position three-way electromagnetic directional valve (3) works at the left position, the oil inlet is communicated with the left position of the two-position three-way electromagnetic directional valve (3) through a through-flow window of the annular valve (1), the pressure oil P is sealed by the left position of the two-position three-way electromagnetic directional valve (3), the oil return port R is communicated with the left position of the two-position three-way electromagnetic directional valve (3) through the through-flow window of the annular valve (1) and is communicated with the left end of the state conversion valve (4), the hydraulic pressure at the left end of the state conversion valve (4) cannot overcome the spring force at the right end of the state conversion valve, and.

4. The hydraulic reversing valve-controlled switching combination valve of claim 1, wherein: the two-position four-way electromagnetic directional valve (2) and the two-position three-way electromagnetic directional valve (3) are connected in parallel in a hydraulic oil circuit, the two-position four-way electromagnetic directional valve (2) in the oil circuit changes the movement direction of the actuating element (7) by controlling the power-on and power-off of the two-position four-way electromagnetic directional valve, the state switching valve (4) controls oil liquid flowing out of a left cavity of the actuating element (7) to generate damping or not to generate damping, and the flow rate of the oil liquid flowing out of the left cavity of the actuating element (7) is controlled to realize the movement speed switching of the; the first damping element (5) and the second damping element (6) damp oil entering or exiting the actuator (7); the first damping element (5) is connected in series with the left chamber of the actuator (7) and the second damping element (6) is connected in series with the right chamber of the actuator (7).

5. The hydraulic reversing valve-controlled switching combination valve of claim 1, wherein: the two-position four-way electromagnetic directional valve (2) and the two-position three-way electromagnetic directional valve (3) are connected with an oil return port R hydraulic pipe and are connected in a hydraulic oil circuit in parallel, the two-position three-way electromagnetic directional valve (3) controls the on and off of the two-position four-way electromagnetic directional valve (2) communicated with the oil inlet P, the station state of the variable state switching valve (4) is switched, the motion direction of the execution element (7) is changed, the state switching valve (4) controls the oil flowing out of the left cavity of the execution element (7) to generate damping or not generate damping and the flow of the oil flowing out of the left cavity through a first damping element (5) connected with the left cavity of the execution element (7), and the motion speed switching of the execution element (7) is realized.

6. The hydraulic reversing valve-controlled switching combination valve of claim 1, wherein: the two-position four-way electromagnetic directional valve (2) is connected with a second damping element (6) on a hydraulic pipeline between an oil return port R of the annular valve (1) and the actuating element (7) in a bypassing mode, and the second damping element (6) is used for damping oil entering or flowing out of a right cavity of the actuating element (7).

7. The hydraulic reversing valve-controlled switching combination valve of claim 1, wherein: the pressure of an oil inlet P of the annular through valve (1) is zero, the annular through valve (1) is communicated with an annular through valve (1) of an actuating element (7) in a two-way mode through a hydraulic pipeline, the pressure P of the oil inlet is rated oil supply pressure, the right end of the annular through valve (1) is communicated with the oil inlet P, the left end of the annular through valve is provided with spring force, and the annular through valve (1) works in the right position under the action of pressure oil P.

8. The hydraulic reversing valve-controlled switching combination valve of claim 1, wherein: the actuating element (7) moves to the left end rapidly and moves to the right end slowly, fluid from a pressure source enables a hydraulic pipeline of an oil inlet P to be communicated with the two-position three-way electromagnetic directional valve (3) through an oil through window of a valve core of the annular valve (1), the two-position three-way electromagnetic directional valve (3) is powered off all the time, the electromagnetic directional valve (3) works in the left position, and pressure oil cannot enter the electromagnetic directional valve (3); the two-position four-way electromagnetic reversing valve (2) is powered off, the electromagnetic reversing valve (2) works in a left position function, the two-position four-way electromagnetic reversing valve (2) connected with the two-position three-way electromagnetic reversing valve (3) in parallel is communicated with an oil port P hydraulic pipeline and a two-position three-way state switching valve (4) through a through flow window of a valve core of the two-position four-way electromagnetic reversing valve, two ends of the two-position three-way state switching valve (4) are communicated with an oil return circuit R, and the state switching valve (4) works in a.

9. The hydraulic reversing valve-controlled switching combination valve of claim 1, wherein: the oil inlet P is communicated with a left cavity of the actuating element (7) through the two-position four-way electromagnetic reversing valve (2) and the state change valve (4), the actuating element (7) moves rightwards under the action of pressure oil, oil in the right cavity of the actuating element (7) returns to the oil return port R through two hydraulic circuits, one oil circuit is communicated with the annular valve (1), and the other oil circuit is connected to the oil return port R through the second directional resistance element (6) and the two-position four-way electromagnetic reversing valve (2).

10. The hydraulic reversing valve-controlled switching combination valve of claim 1, wherein: when the execution element (7) moves towards the left end, the two-position three-way electromagnetic directional valve (3) is powered off all the time, the two-position four-way electromagnetic directional valve (2) is powered on all the time, and the two-position four-way electromagnetic directional valve (2) works at the right position; the oil inlet P is communicated with the right position of the two-position four-way electromagnetic reversing valve (2), pressure oil flows through a valve core through-flow window at the right position of the two-position four-way electromagnetic reversing valve (2), enters the second damping element (6) and enters a right cavity of the actuating element (7), oil in the right cavity of the actuating element (7) reaches the state switching valve (4) through two oil paths, one oil directly reaches the state switching valve through a pipeline, and the other oil reaches the one-way damping valve.