An impact-proof low-hysteresis integrated multi-way valve and a control method thereof

Abstract

The present application relates to a kind of anti-impact low hysteresis integrated multi-way valve and its control method, its valve body uses integral casting, manual hydraulic control general, integrated rotary brake release valve, for rotary motor brake release when manually controlled to provide pressure;Integrated dangerous working condition unloading valve, for the pressure unloading of overload when manually controlled;Integrated standby low pressure unloading valve, for low pressure unloading when standby, unloading noise is small, energy saving;Integrated telescopic switching valve, for the switching of telescopic cylinder control when hydraulic control.Integrated above-mentioned valve simplifies system pipeline connection.Valve after compensation is used, LS pressure acts on compensator spring cavity by the action of damping and one-way valve, compensator opens slowly and closes quickly, both ensure the rapidity of load sensing response, and realize the stability of compensator when compound action.Three-way pressure compensator uses double-spring design, so that shunt valve can be quickly opened, reduce the influence of three-way pressure compensator on main and auxiliary reel, variable amplitude, telescopic work connection hysteresis.

Description

Technical Field

[0001] This invention relates to the field of hydraulic valves, and in particular to an anti-impact, low-hysteresis integrated multi-way valve and its control method. Background Technology

[0002] Multi-way valves are key components of hydraulic systems for construction machinery. Located between the power source and the actuator, they are used to control the direction and flow of hydraulic oil, thereby centrally controlling the movement direction and speed of the machinery's actuators. The performance of multi-way valves directly affects the operability and comfort of the entire system.

[0003] To improve the operating characteristics of multi-way valves, load-sensitive multi-way valves have been developed. These valves incorporate a compensator, which maintains a relatively constant pressure difference across the valve stem throttling orifice. This ensures that the output flow rate depends only on the valve stem opening and is independent of the load, thus improving the operational coordination during compound actions. However, low impact and rapid response cannot be simultaneously achieved, and large hysteresis exists when used in quantitative pump systems.

[0004] Existing crane overhead multi-way valves are divided into integral multi-way valves and plate multi-way valves. Integral multi-way valves typically only integrate the hoisting, luffing, telescopic, and slewing working links. The telescopic switching valve, slewing brake release valve, and hazardous condition unloading valve in the overhead fixed displacement pump load-sensitive system are distributed using functional valve blocks. Furthermore, during standby, the fixed displacement pump flow is unloaded through a three-way pressure compensator. The compensator in the multi-way valve uses a fixed damping buffer.

[0005] The functions of the load-sensitive system of the fixed displacement pump, such as the telescopic switching valve, the rotary brake release valve, and the hazardous condition unloading valve, are arranged in functional valve blocks, which are complex in pipeline connection, costly, and have many leakage and failure points. When the fixed displacement pump load-sensitive system is in standby mode, the pump flow is unloaded through the three-way pressure compensator, which results in high noise and high energy consumption. The working hysteresis of the fixed displacement pump load-sensitive system is affected by the three-way pressure compensator, resulting in large hysteresis. The multi-way valve compensator uses fixed damping buffer, which has a slow response. Summary of the Invention

[0006] The purpose of this invention is to overcome the shortcomings of the prior art and provide an anti-impact, low-hysteresis integrated multi-way valve and its control method.

[0007] To address the problems of existing technologies, this invention discloses an anti-impact, low-hysteresis integrated multi-way valve. The valve body is integrally cast and includes ports D, T1, L, K, LS, P1, P2, T1, and T2. It also includes a first connection, a working connection, and a rotary valve. The first connection includes: a rotary brake release valve, a hazardous condition unloading valve, a standby low-pressure unloading valve, a three-way pressure compensator, a telescopic switching valve, a safety valve, a first damper, a second damper, and a first check valve. A power source, a quantitative pump, is connected to port P1 to provide a constant flow to the multi-way valve. Port P1 is connected to the three-way pressure compensator... The telescopic switching valve, safety valve, and working connection are connected; port T1 is connected to the standby low-pressure unloading valve, three-way pressure compensator, safety valve, and working connection; port LS is connected to the hazardous condition unloading valve, three-way pressure compensator, and working connection, and port LS is connected to port T1 through the second damper and the first damper; port L is connected to the slewing brake release valve, hazardous condition unloading valve, and telescopic switching valve; port K is connected to the slewing brake release valve; port D is connected to the telescopic switching valve; the hazardous condition unloading valve is connected to the standby low-pressure unloading valve; the slewing brake release valve is connected to the working connection; port P2 is connected to the slewing brake release valve through the first check valve.

[0008] Furthermore, the working link includes several links, each link having a pilot oil port and a working oil port, and each link including a main valve core, a compensator and a second check valve; the main valve core is connected to the pilot oil port and the working oil port respectively, the compensator is connected to the main valve core, and the compensator is connected to the swing brake release valve through the second check valve.

[0009] Furthermore, port P1 is connected to port a of the three-way pressure compensator, port a of the telescopic switching valve, one end of the safety valve, and port P of the main valve core; port T1 is connected to port b of the standby low-pressure unloading valve, port b of the three-way pressure compensator, the other end of the safety valve, and port T of the main valve core; port LS is connected to port c of the hazardous condition unloading valve, the spring chamber of the three-way pressure compensator, and port b of the compensator, and port LS is connected to port T1 through the second damper and the first damper; port L is connected to port a of the rotary brake release valve, port a of the hazardous condition unloading valve, and the telescopic switching valve. The main valve core is connected to port b; port K is connected to port c of the rotary brake release valve; port D is connected to port c of the telescopic switching valve; port b of the hazardous condition unloading valve is connected to the spring cavity of the standby low-pressure unloading valve; port P' of the main valve core is connected to port a of the compensator and to port b of the rotary brake release valve through the second check valve; port P” of the main valve core is connected to port c of the compensator; ports A and B of the main valve core are connected to the working oil port; port P2 is connected to port b of the rotary brake release valve through the first check valve; and the pilot oil port is connected to the pilot handle oil port that controls the movement of the main valve core.

[0010] Furthermore, the standby low-pressure unloading valve includes a cone valve, a standby low-pressure unloading valve spring, and a plug. The cone valve has a right chamber and a spring chamber. The pressure at port P1 acts on the right chamber, and the pressure at port LS acts on the spring chamber through the hazardous condition unloading valve. The plug is used to limit the stroke of the cone valve.

[0011] Furthermore, the three-way pressure compensator includes a left screw plug, a first spring, a three-way pressure compensator valve core, a second spring, and a right screw plug. The first spring is located at the left end, and the LS pressure acts on the first spring cavity. The second spring is located at the right end, and the P1 port pressure acts on the second spring cavity. The left and right screw plugs are used to limit the stroke of the three-way pressure compensator valve core. The compression amount of the second spring is the coverage amount of the three-way pressure compensator valve core. From the P1 port to the T port being connected to the P1 port being fully open, the equivalent pressure of the first spring and the second spring is a constant value. When the P1 port to LS pressure is greater than the equivalent pressure of the first spring and the second spring, the three-way pressure compensator opens.

[0012] Furthermore, the compensator includes a plug, a compensator spring, a third check valve, a groove damper, a third damper, and a compensator valve core. The pressure at port P' acts on the lower end of the compensator valve core, and the pressure at port LS acts on the compensator spring cavity through the third check valve, the third damper, and the groove damper. When the compensator valve core reaches a balanced state under the compensator spring, the pressure at port LS, and the pressure at port P', the pressure at port P' is approximately equal to the pressure at port LS. The plug restricts the stroke of the compensator valve core.

[0013] Accordingly, in the above-mentioned control method for the anti-impact low hysteresis integrated multi-way valve, when the pilot handle is not operated, there is no pressure at the pilot port, the main valve core is in the neutral position, the pressure at the P' port of the main valve core is zero, the compensator valve core does not move, the LS pressure is close to zero, the standby low-pressure unloading valve opens, and the oil from the metering pump returns to the T1 port from the standby low-pressure unloading valve.

[0014] Accordingly, in the control method of the above-mentioned anti-impact low-hysteresis integrated multi-way valve, when the single link in the working connection needs to be activated, the pilot handle of the single link is pushed, the pilot port pressure increases, the main valve core reverses, the throttling port from port P to port P' increases to fully open, port P and port P' are connected, pressure is built up at port P', the compensator moves upward under the pressure of port P', port a and port c of the compensator are connected, and at the same time, it is connected to port A or port B of the main valve core, and port a and port b of the compensator are connected, the pressure at port P' is fed back to port LS, and the pressure at port LS acts on the compensator spring cavity through the third check valve, the third damping and the groove damping; the standby low-pressure unloading valve is closed, the three-way pressure compensator is opened, part of the flow rate of the fixed displacement pump flows through the working connection to the working port, and part flows through the three-way pressure compensator back to port T1.

[0015] Accordingly, in the control method of the aforementioned anti-impact low-hysteresis integrated multi-way valve, when two sections in the working link need to perform a combined action, pushing the pilot handles of both sections reverses the main valve cores of both sections, increasing the throttling port from port P to port P' to full opening, thus connecting port P and port P'. Pressure is established at port P', and the compensator moves upward under the pressure at port P'. Ports a and c of the compensator are connected, and simultaneously connected to port A or B of the main valve core. The working oil port pressure of the section with the larger load pressure is fed back to port a of the compensator through port c, causing the compensator of this section to move upward. Ports a and b of the compensator of this section are connected, and the larger load pressure of this section is fed back to port LS. The LS pressure acts on the spring chambers of the compensators of both sections through the third check valve, the third damping, and the groove damping. At this time, ports a and b of the compensator of the section with the smaller load are not connected. The pressure at port P' of this section is approximately equal to the pressure at LS and the pressure at port P' of the section with the larger load. Therefore, the pressure difference before and after the throttling port of the main throttling valve core of both sections is equal. The flow distribution through the two sections depends only on the size of the throttling port of the two sections and is independent of the load.

[0016] Accordingly, in the control method of the aforementioned anti-impact low-hysteresis integrated multi-way valve, when the multi-way valve is manually controlled, port K provides pressure to the rotary brake release valve; when the rotary brake release valve is not energized, port c of the rotary brake release valve is connected to port a, that is, port K is connected to port L, and the rotary brake release pressure is zero; when the rotary brake release valve is energized, port c of the rotary brake release valve is connected to port b, that is, port K is connected to port b of the rotary brake release valve. When there is pressure at port P2, port P2 acts on port b of the rotary brake release valve through the first check valve, and port K is the pressure at port P2, thereby realizing the release of the rotary brake; or when there is pressure at port P' of the main valve core, the pressure at port P' acts on port b of the rotary brake release valve through the second check valve, and port K is the pressure at port P', thereby realizing the release of the rotary brake.

[0017] When the hazardous condition unloading valve is not energized, port c of the hazardous condition unloading valve is connected to port b, meaning that the LS pressure acts on the spring chamber of the standby low-pressure unloading valve, and the LS pressure is not unloaded; when the hazardous condition unloading valve is energized, port c of the hazardous condition unloading valve is connected to port a, meaning that the LS pressure is unloaded to port L through the hazardous condition unloading valve, thereby realizing the unloading of system pressure under hazardous conditions.

[0018] The beneficial effects of this invention are as follows:

[0019] (1) This invention relates to an anti-impact low hysteresis integrated multi-way valve, the valve body of which is integrally cast and integrates main and auxiliary winding, amplitude changing, telescopic working link and rotary valve. It is universal for manual and hydraulic control, making the product easy to process, efficient to process, low risk of leakage and high reliability.

[0020] (2) The present invention integrates a rotary brake release valve into a multi-way valve, which is used to provide pressure for releasing the rotary motor brake during manual control.

[0021] (3) The present invention integrates a multi-way valve for unloading dangerous conditions, which is used for pressure unloading when manually controlled for overload.

[0022] (4) The present invention integrates a multi-way valve with a standby low-pressure unloading valve, which is used to provide low-pressure unloading during standby, with low unloading noise and energy saving.

[0023] (5) The present invention integrates a multi-way valve with a telescopic switching valve for switching the telescopic cylinder control during hydraulic operation. Integrating the above valve simplifies the system piping connection, reduces costs, and minimizes leakage and failure points.

[0024] (6) The multi-way valve of the present invention adopts post-valve compensation. The LS pressure acts on the compensator spring cavity through the damper and the one-way valve. The compensator opens slowly and closes quickly, which not only ensures the fast response of the load sensitivity, but also realizes the stability of the compensator when performing compound actions.

[0025] (7) The three-way pressure compensator in the multi-way valve of the present invention adopts a double spring design, which enables the diversion valve to open quickly and reduces the influence of the three-way pressure compensator on the working hysteresis loop. Attached Figure Description

[0026] Figure 1 This is a schematic diagram of the multi-way valve principle of the present invention;

[0027] Figure 2 This is a schematic diagram of the standby low-pressure unloading valve structure in the multi-way valve of the present invention;

[0028] Figure 3 This is a schematic diagram of the three-way pressure compensator in the multi-way valve of the present invention;

[0029] Figure 4 This is a schematic diagram of the compensator structure in the multi-way valve of the present invention;

[0030] Figure 5 This is a schematic diagram of the groove damping structure of the compensator in the multi-way valve of the present invention.

[0031] Figure label:

[0032] 1. First valve; 2. Working valve; 3. Rotary valve; 4. Rotary brake release valve; 5. Hazardous condition unloading valve; 6. Standby low-pressure unloading valve; 7. Three-way pressure compensator; 8. Telescopic switching valve; 9. Safety valve; 10. First damper; 11. Second damper; 12. Main valve core; 13. Compensator; 14. Second check valve; 15. First check valve;

[0033] Working ports: A1, B1, A2, B2, A3, B3, A4, B4;

[0034] Pilot ports for the working link: a1, b1, a2, b2, a3, b3, a4, b4;

[0035] Oil inlets P1, P2; Oil return outlets T1, T2;

[0036] 6.1. Cone valve; 6.2. Standby low-pressure unloading valve spring; 6.3. Plug;

[0037] 7.1. Left screw plug; 7.2. First spring; 7.3. Three-way pressure compensator valve core; 7.4. Second spring; 7.5. Right screw plug;

[0038] 13.1. Plug; 13.2. Compensator spring; 13.3. Third check valve; 13.4. Groove damper; 13.5. Third damper; 13.6. Compensator valve core. Detailed Implementation

[0039] The present invention will be further described below with reference to the accompanying drawings. The following embodiments are only used to more clearly illustrate the technical solution of the present invention, and should not be used to limit the scope of protection of the present invention.

[0040] like Figure 1 As shown, this invention presents an anti-impact, low-hysteresis integrated multi-way valve. The valve body is integrally cast and has ports D, T1, L, K, LS, P1, P2, T1, and T2. It also includes a first link 1, a working link 2, and a rotary valve 3. The first link 1 includes a rotary brake release valve 4, a hazardous condition unloading valve 5, a standby low-pressure unloading valve 6, a three-way pressure compensator 7, a telescopic switching valve 8, a safety valve 9, a first damper 10, a second damper 11, and a first check valve 15. The working link 2 includes a main winding link, a secondary winding link, a luffing link, and a telescopic link. Each link has the same structure and mainly includes a main valve core 12, a compensator 13, and a second check valve 14.

[0041] The power source quantitative pump is connected to port P1 to provide a constant flow to the multi-way valve. Port P1 is connected to port a of the three-way pressure compensator 7, port a of the telescopic switching valve 8, one end of the safety valve 9, and port P of the main valve core. Port T1 is connected to port b of the standby low-pressure unloading valve 6, port b of the three-way pressure compensator 7, the other end of the safety valve 9, and port T of the main valve core. Port LS is connected to port c of the hazardous condition unloading valve 5, the spring chamber of the three-way pressure compensator 7, and port b of the compensator 13. Port LS is connected to port T1 through the second damper 11 and the first damper 10. Port L is connected to port a of the swing brake release valve 4, port a of the hazardous condition unloading valve 5, and port b of the telescopic switching valve 8. Port K is connected to the return... Port c of the rotary brake release valve 4 is connected; port D is connected to port c of the telescopic switching valve 8; port b of the hazardous condition unloading valve 5 is connected to the spring cavity of the standby low-pressure unloading valve 6; port P' of the main valve core 12 is connected to port a of the compensator 13 and then to port b of the rotary brake release valve 4 via the second check valve 14; port P” of the main valve core 12 is connected to port c of the compensator 13; ports A and B of the main valve core 12 are connected to the working oil port; port P2 is connected to port b of the rotary brake release valve 4 via the first check valve 15 and is used for supplying oil to the rotary valve, while port T2 is used for returning oil to the rotary valve. For the hydraulic multi-way valve, pilot ports a and b are connected to the pilot handle ports that control the movement of the main valve core 12.

[0042] like Figure 2 As shown, the standby low-pressure unloading valve 6 includes a cone valve 6.1, a standby low-pressure unloading valve spring 6.2, and a plug 6.3. The pressure at port P1 acts on the right chamber of the cone valve, and the pressure at port LS acts on the left chamber spring cavity of the cone valve through the hazardous condition unloading valve 5. The plug 6.3 restricts the stroke of the cone valve 6.1. The area of ​​the spring cavity is much larger than the area of ​​the right chamber, and the equivalent pressure of the standby low-pressure unloading valve spring 6.2 is very small.

[0043] like Figure 3 As shown, the three-way pressure compensator 7 includes a left screw plug 7.1, a first spring 7.2, a three-way pressure compensator valve core 7.3, a second spring 7.4, and a right screw plug 7.5. It adopts a double-spring arrangement at both ends. The first spring 7.2 is located at the left end, and the LS pressure acts on the first spring cavity. The second spring 7.4 is located at the right end, and the P1 port pressure acts on the second spring cavity. The left screw plug 7.1 and the right screw plug 7.5 limit the stroke of the three-way pressure compensator valve core. The compression amount of the second spring 7.4 is the coverage amount of the three-way pressure compensator valve core 7.3. From the P1-T connection to the P1-T full opening, the equivalent pressure of the two springs is basically constant. That is, when the P1-LS pressure is greater than the equivalent pressure of the two springs, the three-way pressure compensator 7 opens.

[0044] like Figure 4As shown, the compensator 13 includes a plug 13.1, a compensator spring 13.2, a third check valve 13.3, a groove damper 13.4, a third damper 13.5, and a compensator valve core 13.6. The pressure at port P' acts on the lower end of the compensator valve core 13.6, and the pressure at port LS acts on the compensator spring cavity through the third check valve 13.3, the third damper 13.5, and the groove damper 13.4. The equivalent pressure of the compensator spring 13.2 is very small. Therefore, when the compensator valve core 13.6 reaches a balanced state under the compensator spring 13.2, the pressure at port LS, and the pressure at port P', the pressure at port P' is almost equal to the pressure at port LS. The plug 13.1 and the valve body limit the stroke of the compensator valve core 13.6.

[0045] like Figure 5 As shown, the groove damping 13.4 is a concave groove milled from top to bottom on the outer diameter of the compensator valve core 13.6. The oil in the compensator spring cavity can only flow out through the groove damping 13.4. The oil in the compensator 13 can flow into the compensator spring cavity through the groove damping 13.4, or through the third damping 13.5 and the third one-way valve 13.3, thus realizing the slow opening and fast closing of the compensator.

[0046] Taking a hydraulic multi-way valve as an example, when the pilot handle is not operated, there is no pressure at the pilot port a and port b of the multi-way valve, the main valve core 12 does not switch and is in the neutral position, the pressure at port P' of the main valve core 12 is zero, the compensator valve core 13.6 does not move, the LS pressure is almost zero, and since the equivalent pressure of the standby low-pressure unloading valve spring 6.2 is much smaller than the equivalent pressure of the two springs of the three-way pressure compensator 7, the standby low-pressure unloading valve 6 opens, and the oil from the fixed displacement pump returns to port T1 from the standby low-pressure unloading valve 6, thereby realizing low-pressure unloading of the fixed displacement pump flow during standby, with low noise and low power.

[0047] During single-port operation, the pilot handle of the single-port is gradually pushed, and the pressure at the pilot port a or port b of the multi-way valve gradually increases. The main valve core 12 of the single-port gradually reverses direction, and the throttling port from port P to port P' gradually increases to full opening. Port P and port P' are connected, and pressure is built up at port P'. The compensator 13 moves upward under the pressure at port P'. Ports a and c of the compensator 13 are connected to ports A or B of the main valve core 12, and ports a and b of the compensator 13 are also connected. The pressure at port P' is fed back to port LS. The pressure at port LS acts on the compensator spring chamber through the third check valve 13.3, the third damper 13.5, and the groove damper 13.4. The equivalent pressure of the two springs of the three-way pressure compensator 7 is insufficient to offset the area difference between the spring chamber and the right chamber of the standby low-pressure unloading valve. Therefore, the standby low-pressure unloading valve 6 is closed, and the three-way pressure compensator 7 is opened. At this time, the pressure difference P- across the throttling port of the main valve core is... P' is approximately the equivalent pressure of the two springs of the three-way pressure compensator 7. Therefore, part of the flow from the fixed displacement pump flows through the working connection 2 to the working oil port, and part flows through the three-way pressure compensator back to port T1.

[0048] During the combined operation, the pilot handles of both ports are gradually pushed, causing the main valve cores 12 of both ports to switch directions. The throttling port from port P to port P' gradually increases to full opening, connecting port P and port P'. Pressure is established at port P', and compensator 13 moves upward under the pressure at port P'. Ports a and c of compensator 13 are connected, and simultaneously connected to port A or port B of main valve core 12. The working oil port pressure of the section with the larger load pressure will be fed back to port a of compensator 13 through port c, causing compensator 13 of this section to move upward. Ports a and b of compensator 13 of this section are connected, and the larger load pressure of this section is fed back to port LS. The LS pressure acts on the compensator spring chambers of both sections through the third check valve 13.3, the third damper 13.5, and the groove damper 13.4. At this time, ports a and b of compensator 13 of the section with the smaller load are not connected. The pressure at port P' of this section is almost equal to the pressure at port LS and the pressure at port P' of the section with the larger load. Therefore, the pressure difference before and after the throttling port of the main throttling valve core 12 of both sections is equal. The flow distribution through the two sections is only related to the size of the throttling port of the two sections and is independent of the load.

[0049] When the throttling orifice from port P to port P' of the main valve core 12 gradually increases to fully open, the three-way pressure compensator 7 gradually closes from port a to port b; when the throttling orifice from port P to port P' of the main valve core 12 gradually decreases to close, the three-way pressure compensator 7 gradually opens from port a to port b. The second spring 7.4 of the three-way pressure compensator 7 can make the valve core open quickly, compensating for the friction and hydraulic force during opening and reducing the influence of its multi-operation hysteresis loop.

[0050] When the compensator 13 moves upward to open, the oil in the spring chamber of the compensator 13 can only flow out through the groove damper 13.4 to relieve pressure in the spring chamber, resulting in a slow opening. When the pressure of the heavy load switching LS suddenly changes, causing the compensator 13 to move downward to close, the oil can flow into the spring chamber through the third check valve 13.3, the third damper 13.5, and the groove damper 13.4 to build up pressure and cause the compensator valve core 13.6 to move downward quickly. Therefore, the compensator 13 can achieve slow opening and fast closing, ensuring both fast response to load sensitivity and stability of the compensator during compound actions.

[0051] When the multi-way valve is manually controlled, a rotary brake release valve 4 is installed on the valve body 1. The rotary brake release valve 4 is a two-position three-way solenoid valve. Port K provides pressure for the rotary brake release. When the rotary brake release valve 4 is not energized, port c is connected to port a, that is, port K is connected to port L, and the rotary brake release pressure is zero. When the rotary brake release valve 4 is energized, port c is connected to port b, that is, port K is connected to port b. When there is pressure at the rotary coupling oil inlet port P2, port P2 acts on port b of the rotary brake release valve 4 through the first check valve 15, and port K is the pressure at port P2, thereby releasing the rotary brake. Alternatively, when there is pressure at port P' of the working coupling reversing main valve core, the pressure at port P' acts on port b of the rotary brake release valve 4 through the second check valve 14, and port K is the pressure at port P', thereby releasing the rotary brake.

[0052] When the multi-way valve is manually controlled, a hazardous condition unloading valve 5 is installed on the valve body. The hazardous condition unloading valve 5 is a two-position three-way solenoid valve. When the hazardous condition unloading valve 5 is not energized, port c is connected to port b, that is, the LS pressure acts on the spring chamber of the standby low-pressure unloading valve 6, and the LS pressure is not unloaded. When the hazardous condition unloading valve 5 is energized, port c is connected to port a, that is, the LS pressure is unloaded to port L through the hazardous condition unloading valve 5, thereby realizing the unloading of system pressure under hazardous conditions.

[0053] It should be noted that, in this document, relational terms such as "first" and "second" are used merely to distinguish one entity or operation from another, and do not necessarily require or imply any such actual relationship or order between these entities or operations. Furthermore, the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a process, method, article, or apparatus. Additionally, in the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," and "counterclockwise," indicating orientation or positional relationships, are based on the orientation or positional relationships shown in the accompanying drawings and are only for the convenience of describing the invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the invention. Furthermore, in the accompanying drawings of this invention, the fill patterns are only for distinguishing layers and do not constitute any other limitation.

[0054] Although embodiments of the invention have been shown and described, it will be understood by those skilled in the art that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the invention, the scope of which is defined by the appended claims and their equivalents.

Claims

1. An anti-impact, low-hysteresis integrated multi-way valve, characterized in that, The multi-way valve body is integrally cast and has ports D, T1, L, K, LS, P1, P2, T1, and T2. It also includes a first connection (1), a working connection (2), and a rotary valve (3). The first connection (1) includes: a rotary brake release valve (4), a hazardous condition unloading valve (5), a standby low-pressure unloading valve (6), a three-way pressure compensator (7), a telescopic switching valve (8), a safety valve (9), a first damper (10), a second damper (11), and a first check valve (15). The power source quantitative pump is connected to port P1 to provide a constant flow to the multi-way valve. Port P1 is connected to port a of the three-way pressure compensator (7), port a of the telescopic switching valve (8), one end of the safety valve (9), and the working connection (2). Port T1 is connected to the standby low-pressure unloading valve (6). The b port of the low-pressure unloading valve (6), the b port of the three-way pressure compensator (7), the other end of the safety valve (9), and the working link (2) are connected; the LS port is connected to the c port of the hazardous condition unloading valve (5), the spring cavity of the three-way pressure compensator (7), and the working link (2); the LS port is connected to the T1 port through the second damper (11) and the first damper (10); the L port is connected to the a port of the rotary brake release valve (4), the a port of the hazardous condition unloading valve (5), and the b port of the telescopic switching valve (8); the K port is connected to the c port of the rotary brake release valve (4); the D port is connected to the c port of the telescopic switching valve (8); the b port of the hazardous condition unloading valve (5) is connected to the spring cavity of the standby low-pressure unloading valve (6); the rotary brake release valve (4) is connected to the working link (2); the P2 port is connected to the b port of the rotary brake release valve (4) through the first check valve (15); The standby low-pressure unloading valve (6) includes a cone valve (6.1) and a standby low-pressure unloading valve spring (6.2). The cone valve (6.1) is provided with a right chamber and a spring chamber. The pressure at port P1 acts on the right chamber, and the pressure at port LS acts on the spring chamber through the hazardous condition unloading valve (5). When the hazardous condition unloading valve (5) is not energized, port c of the hazardous condition unloading valve (5) is connected to port b; When the hazardous condition unloading valve (5) is energized, port c of the hazardous condition unloading valve (5) is connected to port a.

2. The anti-impact, low-hysteresis integrated multi-way valve according to claim 1, characterized in that, The working link (2) includes several links, each link is provided with a pilot oil port and a working oil port, and each link includes a main valve core (12), a compensator (13) and a second check valve (14); the main valve core (12) is connected to the pilot oil port and the working oil port respectively, the compensator (13) is connected to the main valve core (12), and the compensator (13) is connected to the slewing brake release valve (4) through the second check valve (14).

3. The anti-impact, low-hysteresis integrated multi-way valve according to claim 2, characterized in that, The P1 port is connected to the P port of the main valve core (12); the T1 port is connected to the T port of the main valve core (12); the LS port is connected to the b port of the compensator (13); the P' port of the main valve core (12) is connected to the a port of the compensator (13) and to the b port of the slewing brake release valve (4) through the second check valve (14); the P” port of the main valve core (12) is connected to the c port of the compensator (13); the A and B ports of the main valve core (12) are connected to the working oil port; the pilot oil port is connected to the pilot handle oil port that controls the action of the main valve core (12).

4. The anti-impact, low-hysteresis integrated multi-way valve according to claim 1, characterized in that, The standby low-pressure unloading valve (6) also includes a plug (6.3) for limiting the stroke of the cone valve (6.1).

5. The anti-impact, low-hysteresis integrated multi-way valve according to claim 1, characterized in that, The three-way pressure compensator (7) includes a left screw plug (7.1), a first spring (7.2), a three-way pressure compensator valve core (7.3), a second spring (7.4), and a right screw plug (7.5). The first spring (7.2) is located at the left end, and the LS pressure acts on the first spring cavity. The second spring (7.4) is located at the right end, and the P1 port pressure acts on the second spring cavity. The left screw plug (7.1) and the right screw plug (7.5) are used to limit the stroke of the three-way pressure compensator valve core (7.3). The compression amount of the second spring (7.4) is the coverage amount of the three-way pressure compensator valve core (7.3). From the P1 port to the T port being connected to the P1-T port being fully open, the equivalent pressure of the first spring (7.2) and the second spring (7.4) is a constant value. When the P1 port-LS pressure is greater than the equivalent pressure of the first spring (7.2) and the second spring (7.4), the three-way pressure compensator (7) opens.

6. The anti-impact, low-hysteresis integrated multi-way valve according to claim 3, characterized in that, The compensator (13) includes a plug (13.1), a compensator spring (13.2), a third check valve (13.3), a groove damper (13.4), a third damper (13.5), and a compensator valve core (13.6). The pressure at port P' acts on the lower end of the compensator valve core (13.6), and the pressure at port LS acts on the compensator spring cavity through the third check valve (13.3), the third damper (13.5), and the groove damper (13.4). When the compensator valve core (13.6) reaches a balanced state under the compensator spring (13.2), the pressure at port LS, and the pressure at port P', the pressure at port P' is approximately equal to the pressure at port LS. The plug (13.1) restricts the stroke of the compensator valve core (13.6).

7. The control method for the anti-impact, low-hysteresis integrated multi-way valve according to claim 6, characterized in that, When the pilot handle is not operated, there is no pressure at the pilot port, the main valve core (12) is in the neutral position, the pressure at the P' port of the main valve core (12) is zero, the compensator valve core (13.6) does not move, the LS pressure is close to zero, the standby low-pressure unloading valve (6) opens, and the oil from the metering pump returns to the T1 port from the standby low-pressure unloading valve (6).

8. The control method for the anti-impact, low-hysteresis integrated multi-way valve according to claim 6, characterized in that, When the single link in the working link (2) needs to be activated, push the pilot handle of the single link, the pilot oil port pressure increases, the main valve core (12) reverses, the throttle port from P port to P' port increases to fully open, P port and P' port are connected, the pressure of P' port is established, the compensator (13) moves upward under the pressure of P' port, the a port of the compensator (13) is connected to the c port, and at the same time connected to the A port or B port of the main valve core (12), and the a port of the compensator (13) is connected to the b port, the pressure of P' port is fed back to the LS port, the LS pressure acts on the compensator spring cavity through the third check valve (13.3), the third damper (13.5) and the groove damper (13.4); the standby low pressure unloading valve (6) is closed, the three-way pressure compensator (7) is opened, part of the flow of the metering pump flows through the working link (2) to the working oil port, and part flows through the three-way pressure compensator (7) back to the T1 port.

9. The control method for the anti-impact, low-hysteresis integrated multi-way valve according to claim 6, characterized in that, When the two sections of the working link (2) need to perform a combined action, push the pilot handle of the two sections, the main valve cores (12) of the two sections reverse, the throttle port from port P to port P' increases to fully open, port P and port P' are connected, pressure is built up at port P', compensator (13) moves upward under the pressure of port P', port a and port c of compensator (13) are connected, and at the same time it is connected to port A or port B of the main valve core (12); the working oil port pressure of the section with the larger load pressure of the two sections is fed back to port a of compensator (13) through port c of compensator (13), causing compensator (13) of this section to move upward, and port a and port b of compensator (13) of this section are connected, and the larger load pressure of this section is fed back to port LS. The LS pressure acts on the spring chambers of the two compensators through the third check valve (13.3), the third damper (13.5) and the groove damper (13.4); at this time, the a port and b port of the compensator (13) of the smaller load are not connected, and the pressure at the P' port of this link is close to the LS pressure and the P' port of the larger load link. Therefore, the pressure difference before and after the throttling port of the main throttling valve core (12) of the two links is equal, and the flow distribution through the two links is only related to the size of the throttling port of the two links and is not related to the load.

10. The control method for the anti-impact, low-hysteresis integrated multi-way valve according to claim 3, characterized in that, When the multi-way valve is manually controlled, port K provides pressure to the rotary brake release valve (4); when the rotary brake release valve (4) is not energized, port c of the rotary brake release valve (4) is connected to port a, that is, port K is connected to port L, and the rotary brake release pressure is zero; when the rotary brake release valve (4) is energized, port c of the rotary brake release valve (4) is connected to port b, that is, port K is connected to port b of the rotary brake release valve (4), when port P2 has pressure, port P2 acts on port b of the rotary brake release valve (4) through the first check valve (15), and port K is the pressure of port P2, thereby realizing the release of the rotary brake; or when port P' of the main valve core (12) has pressure, port P' pressure acts on port b of the rotary brake release valve (4) through the second check valve (14), and port K is the pressure of port P', thereby realizing the release of the rotary brake; When the hazardous condition unloading valve (5) is not energized, port c of the hazardous condition unloading valve (5) is connected to port b, that is, the LS pressure acts on the spring chamber of the standby low pressure unloading valve (6), and the LS pressure is not unloaded; when the hazardous condition unloading valve (5) is energized, port c of the hazardous condition unloading valve (5) is connected to port a, that is, the LS pressure is unloaded to port L through the hazardous condition unloading valve (5), thereby realizing the unloading of system pressure under hazardous conditions.

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