Linear walking system and full-electronic-control linear walking valve

Abstract

The application discloses a straight-line walking system and a full-electric control straight-line walking valve, which can complete a bucket confluence function in a straight-line walking valve core, guarantees a bucket digging speed, can perform reasonable flow control according to speed requirements of each executing mechanism of an excavator under complex working conditions of straight-line walking, guarantees straight-line walking and anti-deviation of the whole machine, and can utilize a hydraulic walking priority valve to make more flow flow into a walking link, thereby guaranteeing a walking priority function. The straight-line walking valve adopts electro-hydraulic proportional control, has multiple function transition positions, including an initial position, a bucket confluence position, a transition position and a straight-line walking position, in a whole stroke process of the valve core, stroke processes can realize functions such as bucket confluence in the valve core, walking anti-deviation and coordinated control of getting on and off under straight-line walking working conditions, meanwhile, the main valve structure is simplified, the overall size is optimized, the manufacturing cost is reduced, and the controllability of the excavator is improved.

Description

TECHNICAL FIELD

[0001] The present application relates to a linear walking system and a full-electric control linear walking valve, belonging to the technical field of engineering machinery. BACKGROUND

[0002] Excavators are widely used in almost all engineering fields due to high technology integration, high efficiency, energy saving, good controllability and multi-functionality. With the development of engineering construction, the working conditions of excavators are becoming more and more complex, which puts forward higher and higher requirements for the controllability of excavators. For medium and large-sized hydraulic excavators above 13T, a double-pump double-circuit hydraulic multi-way main valve is usually used, and when the excavator is in a combined action, reasonable flow distribution is required. Most of the main valves used in excavators use one main pump to supply oil to the left walking, boom 1, bucket and stick 2, and the other main pump to supply oil to the right walking, slewing, boom 2, standby and stick 1. When the two main pumps supply oil to the left and right walking motors respectively, straight-line walking can be easily realized. However, when the excavator is in a working state, since the main pump needs to supply oil to the walking motor and the executing cylinder or slewing motor, it is difficult to ensure equal flow to the left and right walking motors, so it is difficult to realize the straight-line walking function of the excavator, and the deviation is serious.

[0003] For the bucket combined flow working condition, a bucket built-in or externally connected bucket combined flow valve (valve core) is usually used to realize double-pump flow supply to the bucket association, which increases the difficulty of valve body casting. Excavators often work in harsh and complex working conditions, such as excavators sinking in a pit, walking (forward, backward) on a slope with a large slope while working (boom lifting and lowering, bucket digging, stick retracting and swinging, etc.). At this time, the walking speed of the excavator is very slow or the walking stops, and the walking function and coordination of the whole machine are greatly challenged.

[0004] Excavators have many executing mechanisms and complex action working conditions. In order to realize the functions of bucket combined flow, straight-line walking, walking anti-deviation and walking priority, more working associations need to be set and more logic control blocks need to be built-in or externally connected in the valve body to realize the redistribution of system flow and ensure the coordination and controllability of the whole machine. For example, a bucket combined flow association (valve), a priority valve core, a straight-line walking valve core, a bucket logic valve block, a slewing logic valve block and a stick logic valve block are added to the main valve of the excavator.

[0005] The current straight-line walking and walking priority technologies of excavators have the following shortcomings:

[0006] 1. The addition of main valve working associations will cause the main valve structure to be complex, increase the processing difficulty, especially for the throttle control system multi-way valve. At the same time, the addition of main valve working associations will increase the volume of the main valve and increase the manufacturing cost.

[0007] 2. In the existing throttling system, the bucket flow is achieved by the internal bypass cut-off valve and the bucket flow valve, which causes the main valve structure to be complex and the main valve volume to be increased;

[0008] 3. In the load sensing system, the bucket flow is achieved by adding a flow valve block, which causes the main valve structure to be complex and increases the difficulty of the main valve logic control;

[0009] 4. The addition of priority valve cores, bucket logic valve blocks, swing logic valve blocks, and stick logic valve blocks causes the main valve structure to be complex, increases the main valve body volume, and increases the manufacturing cost;

[0010] 5. In the throttling system or load sensing system, the straight travel valve core adopts a long valve core structure and does not have a bucket flow function, the valve core utilization rate is low, and the valve body space is large;

[0011] 6. In the throttling control system multi-way valve, the travel priority function is achieved by setting a travel priority throttling valve, which causes the travel priority throttling valve to always be in a throttling state, reduces the system efficiency, and increases the use cost of the whole machine. SUMMARY

[0012] The technical problem to be solved by the present application is to overcome the defects of the prior art and provide a straight travel system and a full electric control straight travel valve applied to a double pump double circuit hydraulic system, which can complete the bucket flow function inside the straight travel valve core, ensure the bucket digging speed, reasonably control the flow according to the speed demand of each actuator of the excavator during straight travel under complex working conditions, ensure the straight travel and anti-deviation of the whole machine, utilize the hydraulic travel priority valve to make more flow flow into the travel association, and ensure the travel priority function. The straight travel valve adopts electro-hydraulic proportional control, has multiple function transition positions including an initial position, a bucket flow position, a transition position and a straight travel position during the whole stroke of the valve core, can realize functions such as bucket flow inside the valve core, travel anti-deviation and coordinated control of the upper and lower vehicles under straight travel working conditions, simplifies the main valve structure, optimizes the overall size and reduces the manufacturing cost, and improves the controllability of the excavator.

[0013] Meanwhile, the system also has a travel priority function, improves the self-rescue ability of the excavator under complex working conditions, and when the excavator encounters complex working conditions such as deep mud and cross ditch during the working process, the flow is more into the upper vehicle actuator when the travel and the upper vehicle are combined, which causes the travel to be blocked and the whole vehicle to be difficult to complete self-rescue. The system can complete the redistribution of the flow of the travel and the upper vehicle actuator through the hydraulic travel priority valve, make more flow flow into the travel association when the excavator in the mud is combined, improve the self-rescue ability of the excavator, and reduce the throttling loss and improve the system energy efficiency when it is not in the travel priority working condition.

[0014] To achieve the above object, the application provides a straight walking system, comprising hydraulic walking priority valve CT1, CP2 check valve, P1 side and P2 side, the P1 side comprising a first electric control pilot part, a straight walking link, a P1 unloading link, a right walking link, a boom one link, a bucket link, a bucket rod two link, the P2 side comprising a second electric control pilot part, a left walking link, a P2 unloading link, a boom joint link, a boom two link, a boom three link, a rotation link and a bucket rod one link;

[0015] When the full electric control straight walking valve is in the initial position, the hydraulic pump P1 outputs working oil into the first valve body of the full electric control straight walking valve, part of the working oil in the first valve body of the full electric control straight walking valve enters the P1 parallel main oil way of the full electric control straight walking valve through the hydraulic walking priority valve CT1, and the P1 parallel main oil way of the full electric control straight walking valve supplies oil to the boom one link, the bucket link and the bucket rod two link.

[0016] Another part of the working oil in the first valve body of the full electric control straight walking valve enters the straight walking valve core of the full electric control straight walking valve through the P1 main oil way of the full electric control straight walking valve, enters the P1 bypass oil way of the full electric control straight walking valve through the first radial hole of the straight walking valve core and the inclined hole of the straight walking valve core, and the working oil flows into the straight walking link, the right walking link, the boom link, the bucket link and the bucket rod two link through the P1 bypass oil way of the full electric control straight walking valve; the P1 main oil way of the full electric control straight walking valve and the unloading one link oil inlet channel of the full electric control straight walking valve are communicated, and the oil enters the P1 unloading link through the unloading one link oil inlet channel of the full electric control straight walking valve for unloading.

[0017] The hydraulic pump P2 outputs working oil into the second valve body of the full electric control straight walking valve, part of the working oil in the second valve body of the full electric control straight walking valve flows into the left walking link through the P2 main oil way of the full electric control straight walking valve; part of the working oil in the left walking link is branched to the P2 parallel main oil way of the full electric control straight walking valve through the CP2 check valve, supplies oil to the boom joint link, the rotation link and the bucket rod one link, and another part of the working oil in the second valve body of the full electric control straight walking valve flows into the rotation link and the bucket rod one link through the P2 bypass oil way of the full electric control straight walking valve.

[0018] Preferably, when the full electric control straight walking valve is in the bucket joint position, the hydraulic pump P1 outputs working oil into the first valve body of the full electric control straight walking valve, part of the working oil in the first valve body of the full electric control straight walking valve enters the P1 parallel main oil way of the full electric control straight walking valve through the hydraulic walking priority valve CT1, and the P1 parallel main oil way of the full electric control straight walking valve supplies oil to the boom joint link, the boom two link, the bucket link and the bucket rod one link.

[0019] Another part of the working oil in the first valve body of the full electric control linear travel valve enters the P1 bypass oil passage of the full electric control linear travel valve through the P1 main oil passage of the full electric control linear travel valve, the first radial hole of the full electric control linear travel valve, the inclined hole of the full electric control linear travel valve and the third non-full-week throttling hole of the full electric control linear travel valve;

[0020] The working oil entering the P1 bypass oil passage walks to the right travel joint; a part of the working oil in the right travel joint enters the P1 parallel main oil passage of the full electric control linear travel valve through the check valve CP1; another part of the working oil in the right travel joint enters the P1 unloading joint through the unloading-oil-in oil channel of the full electric control linear travel valve to be unloaded;

[0021] The working oil output by the hydraulic pump P2 supplies oil to the first valve body and the second valve body of the full electric control linear travel valve, a part of the working oil in the second valve body of the full electric control linear travel valve flows into the left travel joint through the P2 main oil passage; a part of the working oil in the left travel joint is branched to the P2 parallel main oil passage of the full electric control linear travel valve through the CP2 check valve, and supplies oil to the boom joint, the swing joint and the stick joint;

[0022] Another part of the working oil in the second valve body of the full electric control linear travel valve flows into the swing joint and the stick joint through the P2 bypass oil passage of the full electric control linear travel valve;

[0023] The working oil output by the hydraulic pump P2 enters the first valve body of the full electric control linear travel valve through the connecting oil channel of the full electric control linear travel valve, and the working oil in the first valve body of the full electric control linear travel valve enters the linear travel joint; the working oil in the linear travel joint pushes the valve core plunger of the full electric control linear travel valve through the fourth radial hole of the full electric control linear travel valve, and the working oil in the valve core plunger of the full electric control linear travel valve enters the P1 bypass oil passage of the full electric control linear travel valve through the third radial hole of the full electric control linear travel valve, and the working oil directly enters the P1 bypass oil passage of the full electric control linear travel valve through the second non-full-week throttling hole of the full electric control linear travel valve;

[0024] The working oil in the P1 bypass oil passage of the full electric control linear travel valve inputs the right travel joint; the working oil in the right travel joint enters the P1 parallel main oil passage of the full electric control linear travel valve through the check valve CP1, and the working oil of the hydraulic pump P1 and the hydraulic pump P2 is combined at the P1 parallel main oil passage of the full electric control linear travel valve.

[0025] Preferentially, when the full electric control linear travel valve is in the transition position, the working oil output by the hydraulic pump P1 flows into the first valve body, a part of the working oil in the first valve body enters the P1 parallel main oil passage of the full electric control linear travel valve through the hydraulic travel priority valve CT1, and the P1 parallel main oil passage of the full electric control linear travel valve supplies oil to the boom joint, the bucket joint and the stick joint;

[0026] Another part of the working oil in the first valve body of the full electric control linear walking valve enters the linear walking joint through the P1 main oil path of the full electric control linear walking valve;

[0027] A part of the working oil in the linear walking joint enters the P1 bypass oil path of the full electric control linear walking valve through the first radial hole of the full electric control linear walking valve, the inclined hole of the full electric control linear walking valve and the third non-full circle throttling hole of the full electric control linear walking valve; the working oil in the P1 bypass oil path of the full electric control linear walking valve supplements the right linear walking joint, and the P1 bypass oil path of the full electric control linear walking valve communicates with the joint communication oil path of the full electric control linear walking valve, and the joint communication oil path of the full electric control linear walking valve supplements the left linear walking joint;

[0028] Another part of the working oil in the linear walking joint enters the oil channel of the second valve body of the full electric control linear walking valve through the first non-full circle throttling hole of the full electric control linear walking valve, the first joint communication oil channel of the full electric control linear walking valve and the second joint communication oil channel of the full electric control linear walking valve;

[0029] The oil channel of the full electric control linear walking valve enters the P2 parallel main oil path of the full electric control linear walking valve through the one-way valve CT2, and supplies oil to the boom joint, the swing joint and the arm one joint as an actuator.

[0030] The hydraulic pump P2 outputs working oil to the first valve body of the full electric control linear walking valve and the second valve body of the full electric control linear walking valve, and the working oil entering the second valve body of the full electric control linear walking valve supplies oil to the left linear walking joint through the P2 main oil path of the full electric control linear walking valve; the working oil in the P2 main oil path of the full electric control linear walking valve enters the first valve body of the full electric control linear walking valve through the joint communication oil channel of the full electric control linear walking valve, at this time, the P1 bypass oil path of the full electric control linear walking valve communicates with the joint communication oil path of the full electric control linear walking valve, and a part of the working oil of the first valve body of the full electric control linear walking valve supplements the right linear walking joint;

[0031] Another part of the working oil of the first valve body of the full electric control linear walking valve enters the P1 bypass oil path of the full electric control linear walking valve through the inclined hole of the full electric control linear walking valve, the first radial hole of the full electric control linear walking valve and the third non-full circle throttling hole of the full electric control linear walking valve, and enters the third joint communication oil channel of the second valve body through the first non-full circle throttling hole of the full electric control linear walking valve, the first joint communication oil channel of the full electric control linear walking valve and the second joint communication oil channel of the full electric control linear walking valve;

[0032] The third joint communication oil channel enters the P2 parallel main oil path of the full electric control linear walking valve through the one-way valve CT2, and supplies oil to the boom joint, the swing joint and the arm one joint as an actuator.

[0033] Preferentially, when the full electric control straight travel valve is in straight travel position, the hydraulic pump P1 outputs working oil into the first valve body of the full electric control straight travel valve, part of the working oil in the first valve body of the full electric control straight travel valve enters the P1 parallel main oil path of the full electric control straight travel valve through the hydraulic travel priority valve CT1, and the P1 parallel main oil path of the full electric control straight travel valve supplies oil to the boom one joint, the bucket joint and the arm two joint.

[0034] Another part of the working oil in the first valve body enters the third communication oil path of the second valve body through the P1 main oil path of the full electric control straight travel valve, the first non-full week throttle of the full electric control straight travel valve, the first communication oil path of the full electric control straight travel valve and the second communication oil path of the full electric control straight travel valve, and the working oil in the third communication oil path enters the P2 parallel main oil path of the full electric control straight travel valve after the check valve CT2, and supplies oil to the boom joint, the swing joint and the arm one joint.

[0035] The hydraulic pump P2 outputs working oil to the first valve body of the full electric control straight travel valve and the second valve body of the full electric control straight travel valve, part of the working oil output by the hydraulic pump P2 enters the second valve body of the full electric control straight travel valve, and the P2 main oil path of the second valve body supplies oil to the left travel joint; the working oil of the P2 main oil path of the full electric control straight travel valve enters the first valve body through the communication oil path of the full electric control straight travel valve, the P1 bypass oil path of the full electric control straight travel valve communicates with the communication oil path of the full electric control straight travel valve, and supplies oil to the right travel joint.

[0036] Preferentially, when the full electric control straight travel valve is in non-travel priority position, the pilot oil path oil port (PCt) of the hydraulic travel priority valve CT1 has no pilot pressure, part of the working oil in the P1 main oil path enters the pilot stage oil path of the hydraulic travel priority valve CT1 through the inner spool valve of the hydraulic travel priority valve CT1, reaches the inside of the spool valve core of the hydraulic travel priority valve CT1, and then enters the pilot valve body of the hydraulic travel priority valve CT1 through the second throttle hole of the inner spool valve of the hydraulic travel priority valve CT1, the third throttle hole of the main valve plug of the hydraulic travel priority valve CT1, the first oil groove of the spool valve core of the hydraulic travel priority valve CT1, the second oil groove of the spool valve core of the hydraulic travel priority valve CT1 and the bottom hole of the spool valve spring seat of the hydraulic travel priority valve CT1, the working oil in the pilot valve body of the hydraulic travel priority valve CT1 returns to the P1 parallel main oil path through the sixth communication oil path of the hydraulic travel priority valve CT1, the fifth communication oil path of the hydraulic travel priority valve CT1 and the fourth communication oil path of the hydraulic travel priority valve CT1, and the right end of the spool valve core assembly has no pressure, the working oil in the P1 main oil path pushes away the spool valve core of the hydraulic travel priority valve CT1 and enters the P1 parallel main oil path.

[0037] Preferably, when the walking priority position of the full electric control straight walking valve, the pilot oil port (PCt) of the liquid walking priority valve CT1 is provided with a pilot pressure, the pilot valve core of the liquid walking priority valve CT1 is reversed, and the fifth communication oil channel and the sixth communication oil channel of the liquid walking priority valve CT1 are no longer communicated under the action of the pilot valve core of the liquid walking priority valve CT1.

[0038] The working oil in the P1 main oil channel of the full electric control straight walking valve passes through the inner spool valve of the liquid walking priority valve CT1 to the spool valve core of the liquid walking priority valve CT1, and then enters the pilot valve body of the liquid walking priority valve CT1 through the second throttling hole of the inner spool valve, the third throttling hole of the main valve plug, the first oil groove of the spool valve core, the second oil groove of the spool valve core, and the bottom hole of the spool spring seat of the liquid walking priority valve CT1. At this time, the fifth communication oil channel and the sixth communication oil channel of the liquid walking priority valve CT1 are no longer communicated under the action of the pilot valve core of the liquid walking priority valve CT1, the right end of the spool valve core assembly of the liquid walking priority valve CT1 is pressurized, the spool valve core of the liquid walking priority valve CT1 is closed under the action of the pressure, and the working oil in the P1 main oil channel can only enter the P1 parallel main oil channel of the full electric control straight walking valve through the first throttling hole of the spool valve core.

[0039] The full electric control straight walking valve, the straight walking valve core includes a main valve, a left end reset spring and a stroke limiting device part, and a right valve core, the left end reset spring and the stroke limiting device part are installed on the right valve core; the left end reset spring and the stroke limiting device part and the right valve core are arranged in the main valve;

[0040] The left end reset spring and the stroke limiting device part include a first spring, a second spring, a left spring seat, a right spring seat, a valve core limiting sleeve and a limiting screw, the left spring seat, the first spring, the second spring seat, the valve core limiting sleeve and the right spring seat are sleeved on the limiting screw, and the limiting screw is tightly connected with the positioning hole of the right valve core.

[0041] Preferably, a first necking groove and a second necking groove are arranged on the right valve core, and the first necking groove is located on the left side of the second necking groove.

[0042] A first non-full-circle throttling port is arranged on the right end of the first necking groove in the circumferential direction, a second non-full-circle throttling port is arranged on the right end of the second necking groove in the circumferential direction, and a plurality of third non-full-circle throttling ports are arranged on the left end of the second necking groove in the circumferential direction.

[0043] A plurality of inclined holes are arranged on the left end of the second necking groove towards the valve core axis, the inclined holes are located on the inner side of the third non-full-circle throttling port, part of the inclined holes communicate with the third non-full-circle throttling port, and the number of the inclined holes is less than that of the third non-full-circle throttling port.

[0044] The right valve core is provided with a first radial hole and a fourth radial hole, the first radial hole is located between the first necking groove and the second necking groove, and the fourth radial hole is located on the right side of the second necking groove, and the inclined hole is communicated with the first radial hole;

[0045] The right valve core is provided with a second radial hole on the right side in the axial direction, and the second necking groove is provided with a third radial hole in the radial direction.

[0046] Preferably, a spring and a valve core plunger are included, the valve core plunger is located on the right side of the second radial hole, the spring is located between the valve core plunger and the second radial hole, and the second radial hole, the third radial hole and the fourth radial hole are communicated.

[0047] Preferably, a plug and an O-ring are included, the right valve core is a hollow valve core, and the hollow part at the right end of the right valve core is tightly sealed by the plug and the O-ring.

[0048] Preferably, the main valve includes a first valve body and a second valve body, and the first valve body is located on the lower side of the second valve body.

[0049] The first valve body includes a first pilot unloading oil channel, a first return oil channel, an unloading first joint oil inlet channel, a second return oil channel, a first oil cavity, a P1 parallel main oil path, a third return oil channel, a communication oil path, a P1 bypass oil path, a P1 main oil path, a first communication oil channel, a fourth return oil channel, a second pilot unloading oil channel and a second communication oil channel.

[0050] The first return oil channel, the second return oil channel, the third return oil channel and the fourth return oil channel are communicated in the first valve body; the P1 parallel main oil path, the P1 bypass oil path, the P1 main oil path and the unloading first joint oil inlet channel are communicated in the first valve body.

[0051] Preferably, the second valve body includes a third pilot unloading oil channel, a fifth return oil channel, a left walking joint execution oil port A, a P2 bypass oil path, a P2 parallel main oil path, a second oil cavity, a P2 main oil path, a left walking joint execution oil port B, a sixth return oil channel, a fourth pilot unloading oil channel and a third communication oil channel; the third pilot unloading oil channel, the fifth return oil channel, the first left walking execution oil port, the P2 bypass oil path, the second oil cavity, the P2 main oil path, the second left walking execution oil port, the sixth return oil channel and the fourth pilot unloading oil channel are sequentially communicated from right to left, and the upper end of the second oil cavity is communicated with the P2 parallel main oil path.

[0052] The first communication oil channel is communicated with the second valve body through the second communication oil channel and the third communication oil channel, the first communication oil channel is communicated with the P2 parallel main oil path, the P2 main oil path is communicated with the communication oil path, the third pilot unloading oil channel is communicated with the first pilot unloading oil channel, and the right valve core is inserted into the third return oil channel, the communication oil path, the P1 bypass oil path, the P1 main oil path, the first communication oil channel, the fourth return oil channel and the second pilot unloading oil channel.

[0053] The beneficial effects achieved by the present application are as follows:

[0054] 1、The full electric control straight walking valve in the present application adopts the short valve core structure design of independent control, occupies smaller valve body space, integrates the functions of multi-station main valve, can realize the control of the size and direction of specific working oil flow, and can improve the utilization rate of the valve core.

[0055] 2、The bucket confluence function in the present application is arranged at one of the transition positions of the straight walking valve core, which can increase the space utilization rate of the valve core, avoid the separate arrangement of the bucket confluence valve in the valve body, reduce the oil passage in the valve body, simplify the oil passage of the casting, and reduce the overall machining difficulty.

[0056] 3、The hydraulic oil of the P2 port is subjected to bucket confluence through the valve core plunger inside the straight walking valve core, the valve core spring and the valve core plunger play the role of a one-way valve, the one-way valve is installed in the straight walking valve core, the utilization rate of the valve core is improved, the oil passage in the valve body is reduced, the oil passage of the casting is simplified, and the system impact caused by the backflow of the oil is avoided.

[0057] 4、The transition position of the full electric control straight walking valve in the present application adopts the proportional throttling form, in the process of the function of the straight walking valve from the transition position to the straight walking position, the sudden speed reduction and system impact of the walking association caused by the movement of the valve core of the straight walking valve can be effectively avoided, the control precision is improved, and the overall control performance and coordination are improved.

[0058] 5、The liquid walking priority valve CT1 is arranged in the present application, which can effectively ensure that the pump outlet flow is preferentially distributed to the walking association when the walking association single action and the upper vehicle working device compound action are combined, realizes the walking association action priority, improves the self-rescue ability under special working conditions, and can also prevent the backflow of the P1 side actuator working oil.

[0059] 6、The valve core spring and the valve core plunger are arranged inside the straight walking valve core in the present application, which can effectively complete the oil supplement of the upper vehicle actuator to the lower vehicle walking association when the straight walking valve is actuated, and effectively avoid the walking deviation and system impact caused by the combination of the upper vehicle actuator and the walking association.

[0060] 7、The straight walking valve core throttling position in the present application is in the form of a radial hole and an inclined hole, which can minimize the influence of the liquid dynamic force on the position control precision of the valve core, thereby ensuring the control precision.

[0061] 8、The straight walking association valve core in the present application is relatively short and has a small hollow length, thereby reducing the machining difficulty and the manufacturing cost, shortening the oil passage length of the mutual oil supply of the first valve body and the second valve body, reducing the system pressure loss, and reducing unnecessary power loss.

[0062] 9、The liquid walking priority valve CT1 of the application adopts annular throttling form, and its special structure realizes the functions of throttling and one-way oil inlet simultaneously, improves the space utilization rate of the valve body, and reduces the number of plug-in installations.

[0063] 10、The full electric control linear walking valve and unloading are arranged together in the application, the right end pressure oil of the linear walking valve is unloaded by the cavity of the unloading valve core, the structure of the linear walking valve and the valve body can be effectively simplified, the overall machining difficulty is reduced, and the cost is saved. BRIEF DESCRIPTION OF DRAWINGS

[0064] Figure 1 It is a cross-sectional view of the linear walking valve core structure of the full electric control linear walking valve of the application.

[0065] Figure 2 It is a cross-sectional view of the valve body oil passage of the full electric control linear walking valve of the application.

[0066] Figure 3 It is a cross-sectional view of the valve core and valve body of the full electric control linear walking valve of the application in the initial position.

[0067] Figure 4 It is a cross-sectional view of the valve core and valve body of the full electric control linear walking valve of the application in the bucket confluence position.

[0068] Figure 5 It is a cross-sectional view of the valve core and valve body of the full electric control linear walking valve of the application in the transition position.

[0069] Figure 6 It is a cross-sectional view of the valve core and valve body of the full electric control linear walking valve of the application in the straight walking position.

[0070] Figure 7 It is an outline drawing of the cone valve core assembly of the application.

[0071] Figure 8 It is a cross-sectional view of the liquid walking priority valve CT1 when the walking priority function is closed.

[0072] Figure 9 It is a cross-sectional view of the liquid walking priority valve CT1 when the walking priority function is opened.

[0073] The reference numerals in the attached diagram have the following meanings: 1-Linear travel valve core; 101-First non-full circumferential throttling orifice; 102-First radial hole; 103-Angled hole; 104-Second radial hole; 105-Third radial hole; 106-Fourth radial hole; 107-Second non-full circumferential throttling orifice; 108-Third non-full circumferential throttling orifice; 109-Valve core spring; 110-Valve core plunger; 111-First spring; 112-Second spring; 113-Left spring seat; 114-Right spring seat; 115-Valve core limiting sleeve; 116 - Right valve core; 117- First necking groove; 118- Second necking groove; 119- Plug; 120- O-ring; 121- Limiting screw; 2- First valve body; 201- First pilot unloading oil passage; 202- First return oil passage; 203- Unloading combined inlet oil passage; 204- Second return oil passage; 205- First oil chamber; 206- P1 parallel main oil circuit; 207- Third return oil passage; 208- Connecting oil circuit; 209- P1 bypass oil circuit; 210- P1 main oil circuit; 211- 212-First connecting oil passage, 213-Second pilot unloading oil passage, 214-Second connecting oil passage; 3-Second valve body, 301-Third pilot unloading oil passage, 302-Fifth returning oil passage, 303-Left travel actuator port A, 304-P2 bypass oil passage, 305-P2 parallel main oil passage, 306-Second oil chamber, 307-P2 main oil passage, 308-Left travel actuator port B, 309-Sixth returning oil passage, 310-Fourth pilot unloading oil passage, 311 - Third connecting oil passage; 401-Plug assembly, 402-Pilot spring, 403-Pilot valve core, 404-Pilot valve body, 405-Cone valve spring seat, 406-Cone valve spring, 407-Main valve plug, 408-Cone valve core, 409-Cone valve pilot spring, 410-Inner cone valve, a-First throttling orifice, b-Second throttling orifice, c-Third throttling orifice, d-First oil groove, e-Second oil groove, f-Fourth connecting oil passage, g-Fifth connecting oil passage, h-Sixth connecting oil passage, i-Bottom hole. Detailed Implementation

[0074] The following embodiments are only used to illustrate the technical solutions of the present invention more clearly, and should not be used to limit the scope of protection of the present invention.

[0075] It should be noted that if there are directional indicators (such as up, down, left, right, front, back, etc.) in the embodiments of the present invention, they are only used to explain the relative positional relationship and movement of the components in a certain specific posture. If the specific posture changes, the directional indicator will also change accordingly.

[0076] Furthermore, the use of terms such as "first" and "second" in this invention is for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined with "first" and "second" may explicitly or implicitly include at least one of those features. Additionally, the technical solutions of the various embodiments can be combined with each other, but only on the basis of being achievable by those skilled in the art. If the combination of technical solutions is contradictory or impossible to implement, such a combination of technical solutions should be considered non-existent and not within the scope of protection claimed by this invention.

[0077] To improve the coordination of complex actions, linear travel valves are needed in excavating machinery to control linear travel under complex working conditions. This allows for more reasonable flow distribution, prevents travel deviation, and also has a bucket merging function, thereby better controlling the speed of each actuator. A hydraulic travel priority valve is also installed to distribute more flow to the travel linkage, giving priority to the travel function.

[0078] like Figure 1 As shown, the linear travel valve core is a hollow short valve core composed of different throttling orifices, throttling ports, and a built-in check valve, specifically:

[0079] like Figure 1 As shown, the linear travel valve core is a hollow short valve core composed of different throttling orifices, throttling ports, and a built-in check valve, specifically:

[0080] The linear travel valve core 1 includes a left end return spring and a stroke limit device and a right valve core 116. The left end return spring and the stroke limit device are installed on the right valve core 116 by a limit screw 121. The right valve core 116 has a first necking groove 117 and a second necking groove 118. The first necking groove 117 is located to the left of the second necking groove 118.

[0081] The first necking groove 117 has a first non-full circumferential throttling orifice 101 circumferentially opened at the right end, the second necking groove 118 has a second non-full circumferential throttling orifice 107 circumferentially opened at the right end, and several third non-full circumferential throttling orifices 108 circumferentially opened at the left end.

[0082] Several oblique holes 103 are opened at the left end of the second necking groove 118 toward the valve core axis. The oblique holes 103 are located inside the third non-full circumference throttling orifice 108. Some of the oblique holes 103 are connected to the third non-full circumference throttling orifice 108. The number of oblique holes 103 is less than that of the third non-full circumference throttling orifice 108.

[0083] A first radial hole 102 and a fourth radial hole 106 are provided on the right valve core 116. The first radial hole 102 is located between the first necking groove 117 and the second necking groove 118, and the fourth radial hole 106 is located to the right of the second necking groove 118. The oblique hole 103 communicates with the first radial hole 102.

[0084] A second radial hole 104 is axially opened on the right side of the right valve core 116, and a third radial hole 105 is radially opened on the second necked groove 118.

[0085] The linear travel valve core 1 also includes a spring 109 and a valve core plunger 110. The valve core plunger 110 is located to the right of the second radial hole 104, and the spring 109 is located between the valve core plunger 110 and the second radial hole 104. The second radial hole 104, the third radial hole 105 and the fourth radial hole 106 are connected.

[0086] The left-end reset spring and stroke limiting device includes a first spring 111, a second spring 112, a left spring seat 113, a right spring seat 114, and a valve core limiting sleeve 115. The cross-sections of the left spring seat 113 and the right spring seat 114 are U-shaped, and the valve core limiting sleeve 115 is a circular sleeve. The second spring 112 is sleeved on the left spring seat 113 and the right spring seat 114.

[0087] A positioning hole is axially opened at the left end of the right valve core 116. The left spring seat 113, the first spring 111, the second spring seat 112, the valve core limiting sleeve 115 and the right spring seat 114 are sleeved on the limiting screw 121. The limiting screw 121 is fastened to the positioning hole of the right valve core 116.

[0088] The linear travel valve core 1 also includes a plug 119 and an O-ring 120. The right valve core 116 is a cylindrical rod and a hollow valve core. The hollow part at the right end of the right valve core 116 is fastened and sealed by the plug 119 and the O-ring 120.

[0089] The diameter of the right valve core 116 at the first necking groove 117 and the second necking groove 118 is smaller than the diameter at other parts of the right valve core 116. The spring 109, valve core plunger 110, first spring 111, second spring 112, left spring seat 113, right spring seat 114, O-ring 120, limit screw 121 and limit sleeve 115 are existing technologies.

[0090] The fully electric linear travel valve moves through the linear travel valve core 1. The throttling port and throttling orifice on the linear travel valve core 1 are connected to different oil passages of the valve body, thereby realizing the different working position functions of the linear travel valve under different strokes.

[0091] like Figure 2As shown, the main valve includes a first valve body 2 and a second valve body 3, with the first valve body 2 located below the second valve body 3. The first valve body 2 includes a first pilot unloading oil passage 201, an unloading first-connection oil inlet oil passage 203, a first return oil passage 202, a second return oil passage 204, a third return oil passage 207, a first oil chamber 205, a P1 parallel main oil passage 206, a connecting oil passage 208, a P1 bypass oil passage 209, a P1 main oil passage 210, a first connecting oil passage 211, a fourth return oil passage 212, a second pilot unloading oil passage 213, and a second connecting oil passage 214; the first return oil passage 202, the second return oil passage 204, the third return oil passage 207, and the fourth return oil passage 212 are connected inside the first valve body 2; the P1 parallel main oil passage 206, the P1 bypass oil passage 209, the P1 main oil passage 210, and the unloading first-connection oil inlet oil passage 203 are connected inside the first valve body 2.

[0092] The second valve body 3 oil passage includes a third pilot unloading oil passage 301, a fifth return oil passage 302, a left travel actuator port A 303, a P2 bypass oil passage 304, a P2 parallel main oil passage 305, a second oil chamber 306, a P2 main oil passage 307, a left travel actuator port B 308, a sixth return oil passage 309, a fourth pilot unloading oil passage 310, and a third connecting oil passage 311. The third pilot unloading oil passage 301, the fifth return oil passage 302, the first left travel actuator port 303, the P2 bypass oil passage 304, the second oil chamber 306, the P2 main oil passage 307, the second left travel actuator port 308, the sixth return oil passage 309, and the fourth pilot unloading oil passage 310 are connected sequentially from right to left. The upper end of the second oil chamber 306 is connected to the P2 parallel main oil passage 305.

[0093] The first connecting oil passage 211 connects to the interior of the second valve body 3 via the second connecting oil passage 214 and the third connecting oil passage 311. The first connecting oil passage 211 is connected to the P2 parallel main oil passage 305. The P2 main oil passage 307 is connected to the connecting oil passage 208. The third pilot unloading oil passage 301 is connected to the first pilot unloading oil passage 201. The right valve core 116 is inserted into the third return oil passage 207, the connecting oil passage 208, the P1 bypass oil passage 209, the P1 main oil passage 210, the first connecting oil passage 211, the fourth return oil passage 212, and the second pilot unloading oil passage 213.

[0094] This linear travel valve is used in a dual-pump dual-circuit system, which includes a first valve body 2 and a second valve body 3. By setting the main oil port P to be independently arranged and the main oil supply passage to be a vertically connected passage, the system pressure loss is reduced. By setting positive and negative action check valves to isolate the main oil port P from the actuator in opposite phases, the stability of the system operation is ensured. At the same time, different working links distributed in parallel are equipped with different plug-ins according to different working requirements.

[0095] The P1 side in the prior art includes a first electronic control pilot section, a straight travel link, a P1 unloading link, a right travel link, a boom link, a bucket link, and a stick link.

[0096] The P2 side in the prior art includes the second electronic control pilot section, left travel link, P2 unloading link, boom confluence link, boom second link, boom third link, slewing link, and stick first link.

[0097] During operation, the electronically controlled linear travel valve's full stroke includes the initial position, bucket merging position, transition position, and straight-line position. For example... Figure 3 As shown, the initial function of this linear travel valve is:

[0098] Hydraulic pump P1 outputs working oil into the first valve body 2. A portion of the working oil in the first valve body 2 enters the P1 parallel main oil circuit 206 through the hydraulic travel priority valve CT1. The P1 parallel main oil circuit 206 supplies oil to the boom linkage, bucket linkage and stick linkage, which are the actuators.

[0099] Another portion of the working oil in the first valve body 2 enters the linear travel valve core 1 through the P1 main oil passage 210, and enters the P1 bypass oil passage 209 through the first radial hole 102 and the inclined hole 103. The working oil flows into the linear travel link, right travel link, boom link, bucket link, and stick link through the P1 bypass oil passage 209. The P1 main oil passage 210 and the unloading link inlet oil passage 203 are connected, and the oil enters the P1 unloading link for unloading through the unloading link inlet oil passage 203.

[0100] The hydraulic pump P2 outputs working oil into the second valve body 3. A portion of the working oil in the second valve body 3 flows into the left travel linkage via the P2 main oil passage 307. A portion of the working oil in the left travel linkage is diverted to the P2 parallel main oil passage 305 via the CP2 check valve, supplying oil to the boom confluence linkage, slewing linkage, and stick linkage, which serve as actuators. Another portion of the working oil in the second valve body 3 flows into the slewing linkage and stick linkage via the P2 bypass oil passage 304.

[0101] In the initial working condition, the hydraulic pump P1 supplies working oil only to the actuator connected to the first valve body, and the hydraulic pump P2 supplies working oil only to the actuator connected to the second valve body.

[0102] like Figure 4 As shown, the working function of the linear travel valve at the bucket confluence position is:

[0103] The hydraulic pump P1 outputs working oil into the first valve body 2. A portion of the working oil in the first valve body 2 enters the P1 parallel main oil circuit 206 through the hydraulic travel priority valve CT1. The P1 parallel main oil circuit 206 supplies oil to the boom confluence, boom 2nd link, bucket link and stick 1st link, which are the actuators.

[0104] Another portion of the working oil in the first valve body 2 enters the first radial hole 102, the oblique hole 103 and the third non-full circumference throttling port 108 through the P1 main oil passage 210 and then enters the P1 bypass oil passage 209.

[0105] The working oil entering the P1 bypass oil circuit 209 supplies oil to the right travel link; a portion of the working oil in the right travel link enters the P1 parallel main oil circuit 206 via the check valve CP1. The other portion of the working oil in the right travel link enters the P1 unloading link for unloading through the unloading link inlet oil passage 203.

[0106] Hydraulic pump P2 outputs working oil to supply oil to the first valve body 2 and the second valve body 3. A portion of the working oil in the second valve body 3 flows into the left travel linkage via the P2 main oil passage 307. A portion of the working oil in the left travel linkage is diverted to the P2 parallel main oil passage 305 via the CP2 check valve, supplying oil to the boom confluence linkage, slewing linkage, and stick linkage, which serve as actuators. Another portion of the working oil in the second valve body 3 flows into the slewing linkage and stick linkage through the P2 bypass oil passage 304.

[0107] The hydraulic pump P2 outputs working oil into the first valve body 2 through the connecting oil passage 208. The working oil in the first valve body 2 enters the linear travel link. The working oil in the linear travel link pushes the valve core plunger 110 through the fourth radial hole 106. The working oil in the valve core plunger 110 enters the P1 bypass oil passage 209 through the third radial hole 105. As the valve core stroke continues to open, the working oil directly enters the P1 bypass oil passage 209 through the second non-full circumference throttling port 107.

[0108] The working oil in the P1 bypass oil circuit 209 is input to the right travel link; the working oil in the right travel link enters the P1 parallel main oil circuit 206 through the one-way valve CP1, and the working oil of hydraulic pump P1 and hydraulic pump P2 completes the dual pump confluence at the P1 parallel main oil circuit 206.

[0109] When the linear travel valve is in the working condition of the bucket confluence position, the working oil of hydraulic pump P1 is only supplied to the actuator on the first valve body side; the working oil of hydraulic pump P2 is supplied to both the actuator on the first valve body side and the actuator on the second valve body side. The working oil of hydraulic pump P2 enters the parallel main oil circuit 206 of P1 through the linear travel link and the right travel link, completing the confluence of the two pumps and improving the bucket digging speed.

[0110] like Figure 5 As shown, the working function of this linear travel valve in the transition position is:

[0111] When the linear travel valve is in the transition position, the left travel linkage, right travel linkage, and any one of the upper actuators have been activated. The hydraulic pump P1 outputs working oil into the first valve body 2. A portion of the working oil in the first valve body 2 enters the P1 parallel main oil circuit 206 through the hydraulic control travel priority valve CT1. The P1 parallel main oil circuit 206 supplies oil to the actuator boom linkage, bucket linkage, and stick linkage.

[0112] Another portion of the working oil in the first valve body 2 enters the linear travel link through the P1 main oil passage 210. A portion of the working oil in the linear travel link enters the P1 bypass oil passage 209 through the first radial hole 102, the oblique hole 103, and the third non-full circumference throttling port 108; the working oil in the P1 bypass oil passage 209 replenishes the right travel link, and at the same time, the P1 bypass oil passage 209 is connected to the connecting oil passage 208, and the connecting oil passage 208 replenishes the left travel link;

[0113] Another part of the working oil in the straight-line travel joint enters the oil passage 311 of the second valve body 3 through the first non-full-circuit throttle port 101, the first connecting oil passage 211 and the second connecting oil passage 214.

[0114] Oil passage 311 enters the P2 parallel main oil passage 305 via check valve CT2, supplying oil to the boom confluence, slewing, and stick linkages, which serve as actuators.

[0115] Hydraulic pump P2 outputs working oil to supply oil to the first valve body 2 and the second valve body 3. The working oil entering the second valve body 3 travels to the left via the P2 main oil passage 307 for joint oil supply. The working oil in the P2 main oil passage 307 enters the first valve body 2 via the connecting oil passage 208. At this time, the P1 bypass oil passage 209 is connected to the connecting oil passage 208, and a portion of the working oil in the first valve body 2 travels to the right for joint oil replenishment.

[0116] Another part of the working oil of the first valve body 2 enters the P1 bypass oil passage 209 through the inclined hole 103, the first radial hole 102, and the third non-full circumference throttling port 108, and enters the third connecting oil passage 311 of the second valve body 3 through the first non-full circumference throttling port 101, the first connecting oil passage 211, and the second connecting oil passage 214.

[0117] The third connecting oil passage 311 enters the P2 parallel main oil passage 305 via the one-way valve CT2, supplying oil to the boom confluence, slewing, and stick linkages, which serve as actuators.

[0118] When the linear travel valve is in the transition position, hydraulic pump P1 outputs hydraulic oil to power the upper actuator and can replenish oil to the left and right travel links of the lower vehicle via the linear travel link; hydraulic pump P2 outputs working oil to power the left and right travel links of the lower vehicle and can supply oil to the upper actuator of the second valve body via the linear travel link; the linear travel valve effectively replenishes oil to the lower travel link by electro-proportional control of the working oil of hydraulic pump P1, which has a good effect on preventing the travel from deviating.

[0119] like Figure 6 As shown, the working function of this linear travel valve in the linear travel position is as follows:

[0120] When the linear travel valve is in the straight travel position, the left travel linkage, right travel linkage, and any one of the upper actuators have been activated. The hydraulic pump P1 outputs working oil into the first valve body 2. A portion of the working oil in the first valve body 2 enters the P1 parallel main oil circuit 206 through the hydraulic control travel priority valve CT1. The P1 parallel main oil circuit 206 supplies oil to the boom linkage, bucket linkage, and stick linkage, which serve as actuators.

[0121] Another portion of the working oil in the first valve body 2 enters the third connecting oil passage 311 of the second valve body 3 through the P1 main oil passage 210, the first non-full circumference throttle port 101, the first connecting oil passage 211, and the second connecting oil passage 214. The working oil in the third connecting oil passage 311 enters the P2 parallel main oil passage 305 after passing through the check valve CT2, and supplies oil to the boom confluence, slewing, and stick linkages, which serve as actuators.

[0122] Hydraulic pump P2 outputs working oil to supply oil to the first valve body 2 and the second valve body 3. A portion of the working oil output by hydraulic pump P2 enters the second valve body 3, and the P2 main oil circuit 307 of the second valve body 3 supplies oil to the left. The working oil from the P2 main oil circuit 307 enters the first valve body 2 via the connecting oil passage 208. The P1 bypass oil circuit 209 is connected to the connecting oil circuit 208 and supplies oil to the right. When the linear travel valve is in the straight travel position, hydraulic pump P1 outputs hydraulic oil to supply hydraulic oil for the upper actuator; hydraulic pump P2 outputs working oil to supply hydraulic oil for the lower actuator.

[0123] Figure 7 This is an outline drawing of the cone valve core assembly. Figure 8 This is a cross-sectional view of the hydraulically controlled travel priority valve CT1. The working function of the non-travel priority position is as follows:

[0124] With no pilot pressure at the pilot oil port PCt, a portion of the working oil in the P1 main oil circuit 210 enters the pilot stage oil circuit of the hydraulic travel priority valve CT1 through the inner cone valve 410, reaches the inside of the cone valve core 408, and then enters the pilot valve body 404 through the second throttle hole b of the inner cone valve 410, the third throttle hole c of the main valve plug 407, the first oil groove d of the cone valve core 408, the second oil groove e of the cone valve core 408, and the bottom hole i of the cone valve spring seat 405. The working oil in the pilot valve body 404 returns to the P1 parallel main oil circuit 206 through the sixth connecting oil passage h, the fifth connecting oil passage g, and the fourth connecting oil passage f. With no pressure buildup at the right end of the cone valve core assembly, the working oil in the P1 main oil circuit 210 pushes open the cone valve core 408 and enters the P1 parallel main oil circuit 206. At this time, the cone valve core 408 acts as a one-way cone valve.

[0125] like Figure 9 As shown, the working function of the walking priority position is:

[0126] Pilot pressure is provided to the pilot oil port PCt, and the pilot valve core 403 reverses. The fifth connecting oil passage g and the sixth connecting oil passage h are no longer connected under the action of the pilot valve core 403. Part of the working oil in the P1 main oil passage 210 enters the pilot stage oil passage of the hydraulic travel priority valve CT1 through the inner cone valve 410, and reaches the inside of the cone valve core 408. The working oil in the cone valve core 408 then enters the pilot valve body 404 through the second throttle orifice b of the inner cone valve 410, the third throttle orifice c of the main valve plug 407, the first oil groove d of the cone valve core 408, the second oil groove e of the cone valve core 408, and the bottom hole i of the cone valve spring seat 405. At this time, the fifth connecting oil passage g and the sixth connecting oil passage h are connected by the pilot valve core 403. When the connection is broken under the action of 03, the right end of the cone valve core 408 assembly is pressurized and the cone valve core 408 is closed under pressure. The working oil in the P1 main oil circuit 210 can only enter the P1 parallel main oil circuit 206 through the first throttle hole a of the cone valve core 408. At this time, the cone valve core 408 acts as a one-way throttle cone valve. When the right travel linkage, boom linkage 1 linkage and stick linkage 2 linkage are combined, it is beneficial for the working oil in the P1 main oil circuit 210 to flow into the right travel linkage, thereby playing the role of travel priority and improving the excavator's self-rescue capability.

[0127] The hydraulic travel priority valve CT1 and CP2 check valve are among the many models that can be used in the prior art. Those skilled in the art can select the appropriate model according to actual needs. This embodiment will not list them all.

[0128] The purpose of this invention is to provide a linear travel valve and its subsystem adapted to the energy regeneration system of a fully electro-hydraulic excavator. This linear travel valve and subsystem are applied to a dual-pump, dual-circuit hydraulic system. They enable bucket merging within the linear travel valve core, ensuring bucket digging speed; they allow for reasonable flow control based on the speed requirements of each actuator during linear travel under complex excavator operating conditions, ensuring straight-line travel and preventing deviation; and they utilize a hydraulically controlled travel priority valve to allow more flow into the travel linkage, ensuring travel priority functionality. This linear travel valve employs electro-hydraulic proportional control and features multiple functional transition positions throughout the valve core's movement, including an initial position, bucket merging position, transition position, and straight-line position. The stroke process enables functions such as bucket merging within the valve core, travel deviation prevention, and coordinated control of loading and unloading during linear travel. Simultaneously, it simplifies the main valve structure, optimizes overall dimensions, reduces manufacturing costs, and improves the excavator's maneuverability.

[0129] This system also features a travel priority function, enhancing the excavator's self-rescue capability in complex working conditions. When an excavator encounters difficult situations such as being deeply mired in mud or ditches, and the travel and overhead mechanisms are engaged in a combined operation, the heavier travel load can cause more flow to the overhead actuators, obstructing travel and making self-rescue difficult. This system, through a hydraulically controlled travel priority valve, redistributes the flow between the travel and overhead actuators, ensuring that when the excavator is engaged in a muddy situation, more flow flows to the travel linkage, improving the excavator's self-rescue capability. Furthermore, in non-travel priority operating conditions, it reduces throttling losses and improves system energy efficiency.

[0130] This invention provides a linear travel valve and linear travel system adapted to the energy regeneration system of a fully electro-hydraulic excavator. The linear travel valve and system are applied to a dual-pump, dual-circuit hydraulic system. They can complete the bucket merging function within the linear travel valve core, ensuring bucket digging speed; they can perform reasonable flow control according to the speed requirements of each actuator during linear travel under complex working conditions of the excavator, ensuring the machine's linear travel and preventing deviation; and they can utilize a hydraulically controlled travel priority valve to allow more flow into the travel linkage, ensuring the travel priority function.

[0131] The linear travel valve of this invention adopts electro-hydraulic proportional control. During the entire stroke of the valve core, it has multiple functional transition positions, including the initial position, the bucket merging position, the transition position, and the straight travel position. During the stroke, it can realize functions such as bucket merging inside the valve core, anti-deviation control during travel, and coordinated control of getting on and off the vehicle under linear travel conditions. At the same time, it simplifies the main valve structure, optimizes the overall size, reduces manufacturing costs, and improves the maneuverability of the excavator.

[0132] In complex working conditions such as when the excavator is deeply stuck in mud or ditches, and the traveling and overhead mechanisms are operating simultaneously, the heavy load on the traveling mechanism causes more flow to flow into the overhead mechanism, obstructing travel and making it difficult for the excavator to extricate itself. This invention addresses this by using a hydraulically controlled traveling priority valve to redistribute the flow between the traveling and overhead mechanisms. This ensures that when the excavator is in mud, more flow flows into the traveling mechanism, improving its self-rescue capability. Furthermore, in non-traveling priority conditions, it reduces throttling losses and improves system energy efficiency.

[0133] Key term definitions:

[0134] Flow confluence --- For hydraulic systems supplied with oil by two or more main pumps, in order to meet the speed requirements of the actuator, it is usually necessary for two or more pumps to supply oil to the actuator at the same time, that is, to achieve flow confluence.

[0135] Travel Priority – When travel is combined with working devices such as boom, stick, and bucket, in order to ensure travel speed, the system flow is preferentially allocated to the travel linkage through priority valves and other devices, thereby achieving travel priority.

[0136] Linear travel valve – When the left and right travel and boom and other overhead devices are operated simultaneously, the valve core actuates to ensure that the flow rate supplied to the left and right travel motors is equal, and the motors rotate at the same speed, ensuring that the whole machine travels in a straight line and preventing deviation.

[0137] The above description is only a preferred embodiment of the present invention. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present invention, and these improvements and modifications should also be considered within the scope of protection of the present invention.

Claims

1. A fully electrically controlled linear travel valve, comprising a main valve and a linear travel valve core, characterized in that, The linear travel valve core includes a left-end return spring and a stroke limit device and a right valve core. The left-end return spring and the stroke limit device are mounted on the right valve core. The left-end return spring and the stroke limit device and the right valve core are located in the main valve. The left end reset spring and stroke limit device includes a first spring, a second spring, a left spring seat, a right spring seat, a valve core limit sleeve, and a limit screw. The left spring seat, the first spring, the second spring, the valve core limit sleeve, and the right spring seat are sleeved on the limit screw, and the limit screw is fastened to the positioning hole of the right valve core. The right valve core has a first necking groove and a second necking groove, with the first necking groove located to the left of the second necking groove. The first non-full-circumference throttling orifice is opened circumferentially at the right end of the first necking groove, the second non-full-circumference throttling orifice is opened circumferentially at the right end of the second necking groove, and several third non-full-circumference throttling orifices are opened circumferentially at the left end of the second necking groove. Several oblique holes are opened at the left end of the second neck groove toward the valve core axis. The oblique holes are located inside the third non-full circumference throttling orifice. Some of the oblique holes are connected to the third non-full circumference throttling orifice. The number of oblique holes is less than that of the third non-full circumference throttling orifice. The right valve core has a first radial hole and a fourth radial hole. The first radial hole is located between the first and second necking grooves, and the fourth radial hole is located to the right of the second necking groove. The oblique hole is connected to the first radial hole. A second radial hole is opened on the right side of the right valve core, and a third radial hole is opened on the second necked groove. The main valve includes a first valve body and a second valve body, with the first valve body located below the second valve body; The first valve body includes a first pilot unloading oil passage, a first return oil passage, an unloading combined inlet oil passage, a second return oil passage, a first oil chamber, a P1 parallel main oil passage, a third return oil passage, a connecting oil passage, a P1 bypass oil passage, a P1 main oil passage, a first connecting oil passage, a fourth return oil passage, a second pilot unloading oil passage, and a second connecting oil passage. The first return oil passage, the second return oil passage, the third return oil passage, and the fourth return oil passage are connected inside the first valve body; the P1 parallel main oil passage, the P1 bypass oil passage, the P1 main oil passage, and the unloading integrated oil inlet passage are connected inside the first valve body. The second valve body includes a third pilot unloading oil passage, a fifth return oil passage, a left travel actuator port A, a P2 bypass oil passage, a P2 parallel main oil passage, a second oil chamber, a P2 main oil passage, a left travel actuator port B, a sixth return oil passage, a fourth pilot unloading oil passage, and a third connecting oil passage; the third pilot unloading oil passage, the fifth return oil passage, the first left travel actuator port, the P2 bypass oil passage, the second oil chamber, the P2 main oil passage, the second left travel actuator port, the sixth return oil passage, and the fourth pilot unloading oil passage are connected sequentially from right to left, and the upper end of the second oil chamber is connected to the P2 parallel main oil passage; The first connecting oil passage is connected to the interior of the second valve body through the second connecting oil passage and the third connecting oil passage. The first connecting oil passage is connected to the main oil circuit parallel to P2. The main oil circuit of P2 is connected to the connecting oil circuit. The third pilot unloading oil passage is connected to the first pilot unloading oil passage. The right valve core is inserted into the third return oil passage, the connecting oil circuit, the P1 bypass oil circuit, the P1 main oil circuit, the first connecting oil passage, the fourth return oil passage, and the second pilot unloading oil passage.

2. The fully electrically controlled linear travel valve according to claim 1, characterized in that, It includes a spring and a valve core plunger. The valve core plunger is located to the right of the second radial hole, and the spring is located between the valve core plunger and the second radial hole. The second radial hole, the third radial hole, and the fourth radial hole are connected.

3. The fully electrically controlled linear travel valve according to claim 1, characterized in that, Includes a plug and an O-ring. The right valve core is a hollow valve core, and the hollow part at the right end of the right valve core is tightened and sealed by the plug and the O-ring.

4. A linear travel system, comprising a P1 side and a P2 side, wherein the P1 side includes a first electronically controlled pilot section, a linear travel linkage, a P1 unloading linkage, a right travel linkage, a boom linkage, a bucket linkage, and a stick linkage; and the P2 side includes a second electronically controlled pilot section, a left travel linkage, a P2 unloading linkage, a boom merging linkage, a boom linkage, a boom linkage, a boom trip linkage, a slewing linkage, and a stick linkage; characterized in that, The linear travel system further includes hydraulically controlled travel priority valves CT1 and CP2 check valves and the fully electrically controlled linear travel valve as described in any one of claims 1 to 3; When the fully electric linear travel valve is in the initial position, the hydraulic pump P1 outputs working oil into the first valve body of the fully electric linear travel valve. A portion of the working oil in the first valve body of the fully electric linear travel valve enters the P1 parallel main oil circuit of the fully electric linear travel valve through the hydraulic travel priority valve CT1. The P1 parallel main oil circuit of the fully electric linear travel valve supplies oil to the boom linkage, bucket linkage and stick linkage. Another portion of the working oil in the first valve body of the fully electric linear travel valve enters the linear travel valve core of the fully electric linear travel valve through the P1 main oil circuit of the fully electric linear travel valve. It then enters the P1 bypass oil circuit of the fully electric linear travel valve through the first radial hole and the oblique hole of the linear travel valve core. The working oil flows into the linear travel linkage, right travel linkage, boom linkage, bucket linkage, and stick linkage through the P1 bypass oil circuit of the fully electric linear travel valve. The P1 main oil circuit of the fully electric linear travel valve is connected to the unloading linkage inlet oil passage of the fully electric linear travel valve. The oil enters the P1 unloading linkage for unloading through the unloading linkage inlet oil passage of the fully electric linear travel valve. The hydraulic pump P2 outputs working oil into the second valve body of the fully electric linear travel valve. A portion of the working oil in the second valve body of the fully electric linear travel valve flows into the left travel linkage via the P2 main oil circuit of the fully electric linear travel valve. A portion of the working oil in the left travel linkage is diverted through the CP2 check valve to the P2 parallel main oil circuit of the fully electric linear travel valve, supplying oil to the boom confluence linkage, slewing linkage, and stick linkage. Another portion of the working oil in the second valve body of the fully electric linear travel valve flows into the slewing linkage and stick linkage through the P2 bypass oil circuit of the fully electric linear travel valve.

5. A linear walking system according to claim 4, characterized in that, When the fully electric linear travel valve is in the bucket confluence position, the hydraulic pump P1 outputs working oil into the first valve body of the fully electric linear travel valve. A portion of the working oil in the first valve body of the fully electric linear travel valve enters the P1 parallel main oil circuit of the fully electric linear travel valve through the hydraulic travel priority valve CT1. The P1 parallel main oil circuit of the fully electric linear travel valve supplies oil to the boom confluence link, boom link 2 link, bucket link and stick link 1 link. Another part of the working oil in the first valve body of the fully electric linear travel valve enters the first radial hole, the oblique hole, and the third non-full circumference throttling port of the fully electric linear travel valve through the P1 main oil circuit of the fully electric linear travel valve and enters the P1 bypass oil circuit of the fully electric linear travel valve. The working oil entering the P1 bypass oil circuit supplies oil to the right travel link; a portion of the working oil in the right travel link enters the P1 parallel main oil circuit of the fully electric linear travel valve through the check valve CP1; another portion of the working oil in the right travel link enters the P1 unloading link for unloading through the unloading link inlet oil passage of the fully electric linear travel valve. Hydraulic pump P2 outputs working oil to supply oil to the first valve body and the second valve body of the fully electric linear travel valve. A portion of the working oil in the second valve body of the fully electric linear travel valve flows into the left travel linkage via the P2 main oil circuit. A portion of the working oil in the left travel linkage is diverted to the P2 parallel main oil circuit of the fully electric linear travel valve via the CP2 check valve, supplying oil to the boom confluence linkage, slewing linkage, and stick linkage. Another portion of the working oil in the second valve body of the fully electric linear travel valve flows into the slewing coupling and the boom coupling through the P2 bypass oil circuit of the fully electric linear travel valve. The hydraulic pump P2 outputs working oil, which enters the first valve body of the fully electric linear travel valve through the connecting oil passage. The working oil in the first valve body of the fully electric linear travel valve enters the linear travel coupling. The working oil in the linear travel coupling pushes the valve core plunger of the fully electric linear travel valve through the fourth radial hole. The working oil in the valve core plunger of the fully electric linear travel valve enters the P1 bypass oil circuit of the fully electric linear travel valve through the third radial hole. The working oil directly enters the P1 bypass oil circuit of the fully electric linear travel valve through the second non-full circumference throttling port. The working oil in the P1 bypass oil circuit of the fully electric linear travel valve is input to the right travel link; the working oil in the right travel link enters the P1 parallel main oil circuit of the fully electric linear travel valve through the check valve CP1, and the working oil of hydraulic pump P1 and hydraulic pump P2 are combined at the P1 parallel main oil circuit of the fully electric linear travel valve.

6. A linear walking system according to claim 4, characterized in that, When the fully electric linear travel valve is in the transition position, the hydraulic pump P1 outputs working oil into the first valve body. A portion of the working oil in the first valve body enters the P1 parallel main oil circuit of the fully electric linear travel valve through the hydraulic travel priority valve CT1. The P1 parallel main oil circuit of the fully electric linear travel valve supplies oil to the boom linkage, bucket linkage and stick linkage. Another portion of the working oil in the first valve body of the fully electronically controlled linear travel valve enters the linear travel linkage through the P1 main oil circuit of the fully electronically controlled linear travel valve. A portion of the working oil in the linear travel link enters the P1 bypass oil circuit of the fully electric linear travel valve through the first radial hole, the inclined hole, and the third non-full circumference throttling port of the fully electric linear travel valve; the working oil in the P1 bypass oil circuit of the fully electric linear travel valve replenishes the right travel link, and at the same time, the P1 bypass oil circuit of the fully electric linear travel valve is connected to the connecting oil circuit of the fully electric linear travel valve, and the connecting oil circuit of the fully electric linear travel valve replenishes the left travel link; Another part of the working oil in the linear travel connection enters the oil passage of the second valve body of the fully electric linear travel valve through the first non-full-circuit throttling port of the fully electric linear travel valve, the first connecting oil passage of the fully electric linear travel valve, and the second connecting oil passage of the fully electric linear travel valve. The oil passage of the fully electric linear travel valve enters the P2 parallel main oil circuit of the fully electric linear travel valve through the CP2 check valve, and supplies oil to the boom confluence, slewing and stick connections. The hydraulic pump P2 outputs working oil to supply oil to the first valve body and the second valve body of the fully electric linear travel valve. The working oil entering the second valve body of the fully electric linear travel valve is supplied to the left travel linkage via the P2 main oil circuit of the fully electric linear travel valve. The working oil in the P2 main oil circuit of the fully electric linear travel valve enters the first valve body of the fully electric linear travel valve through the connecting oil passage of the fully electric linear travel valve. At this time, the P1 bypass oil circuit of the fully electric linear travel valve is connected to the connecting oil circuit of the fully electric linear travel valve, and a part of the working oil in the first valve body of the fully electric linear travel valve moves to the right to replenish the oil. Another part of the working oil of the first valve body of the fully electric linear travel valve enters the P1 bypass oil circuit of the fully electric linear travel valve through the oblique hole, the first radial hole and the third non-full circumference throttling port of the fully electric linear travel valve, and then enters the third connecting oil passage of the second valve body through the first non-full circumference throttling port, the first connecting oil passage and the second connecting oil passage of the fully electric linear travel valve. The third connecting oil passage enters the P2 parallel main oil circuit of the fully electronically controlled linear travel valve via the CP2 check valve, supplying oil to the boom confluence, slewing, and stick linkages, which serve as actuators.

7. A linear walking system according to claim 4, characterized in that, When the fully electric linear travel valve is in the straight travel position, the hydraulic pump P1 outputs working oil into the first valve body of the fully electric linear travel valve. A portion of the working oil in the first valve body of the fully electric linear travel valve enters the P1 parallel main oil circuit of the fully electric linear travel valve through the hydraulic travel priority valve CT1. The P1 parallel main oil circuit of the fully electric linear travel valve supplies oil to the boom linkage, bucket linkage and stick linkage. Another portion of the working oil in the first valve body enters the third connecting oil passage of the second valve body through the P1 main oil passage of the fully electric linear travel valve, the first non-full circumference throttle port of the fully electric linear travel valve, the first connecting oil passage of the fully electric linear travel valve, and the second connecting oil passage of the fully electric linear travel valve. The working oil in the third connecting oil passage enters the P2 parallel main oil passage of the fully electric linear travel valve after passing through the CP2 check valve, and supplies oil to the boom confluence, slewing, and stick connection. Hydraulic pump P2 outputs working oil to supply oil to the first valve body and the second valve body of the fully electric linear travel valve. A portion of the working oil output by hydraulic pump P2 enters the second valve body of the fully electric linear travel valve, and the P2 main oil circuit of the second valve body supplies oil to the left travel linkage. The working oil of the P2 main oil circuit of the fully electric linear travel valve enters the first valve body through the connecting oil passage of the fully electric linear travel valve. The P1 bypass oil circuit of the fully electric linear travel valve is connected to the connecting oil circuit of the fully electric linear travel valve, and oil is supplied to the right for travel.

8. A linear walking system according to claim 4, characterized in that, When the fully electric linear travel valve is in the non-travel priority position, there is no pilot pressure at the pilot oil port PCt of the hydraulic travel priority valve CT1. A portion of the working oil in the P1 main oil circuit enters the pilot stage oil circuit of the hydraulic travel priority valve CT1 through the inner cone valve, reaches the inside of the cone valve core of the hydraulic travel priority valve CT1, and then passes through the second throttle orifice of the inner cone valve of the hydraulic travel priority valve CT1, the third throttle orifice of the main valve plug of the hydraulic travel priority valve CT1, the first oil groove of the cone valve core of the hydraulic travel priority valve CT1, and the hydraulic travel priority valve CT1... The second oil groove of the cone valve core of 1 and the bottom hole of the cone valve spring seat of the hydraulic travel priority valve CT1 enter the pilot valve body of the hydraulic travel priority valve CT1. The working oil in the pilot valve body of the hydraulic travel priority valve CT1 returns to the P1 parallel main oil circuit through the sixth connecting oil passage, the fifth connecting oil passage and the fourth connecting oil passage of the hydraulic travel priority valve CT1. There is no pressure buildup at the right end of the cone valve core assembly. The working oil in the P1 main oil circuit pushes open the cone valve core of the hydraulic travel priority valve CT1 and enters the P1 parallel main oil circuit.

9. A linear walking system according to claim 4, characterized in that, When the fully electric linear travel valve is in the travel priority position, it provides pilot pressure to the pilot oil port PCt of the hydraulic travel priority valve CT1. The pilot valve core of the hydraulic travel priority valve CT1 reverses, and the fifth and sixth connecting oil passages of the hydraulic travel priority valve CT1 are no longer connected under the action of the pilot valve core of the hydraulic travel priority valve CT1. Part of the working oil in the P1 main oil circuit of the fully electronically controlled linear travel valve passes through the inner cone valve of the hydraulic travel priority valve CT1 to the cone valve core of the hydraulic travel priority valve CT1. The working oil in the cone valve core of the hydraulic travel priority valve CT1 then passes through the second throttle orifice of the inner cone valve of the hydraulic travel priority valve CT1, the third throttle orifice of the main valve plug of the hydraulic travel priority valve CT1, the first oil groove of the cone valve core of the hydraulic travel priority valve CT1, the second oil groove of the cone valve core of the hydraulic travel priority valve CT1, and the bottom hole of the cone valve spring seat of the hydraulic travel priority valve CT1. When the pilot valve body of the hydraulic travel priority valve CT1 is entered, the fifth and sixth connecting oil passages of the hydraulic travel priority valve CT1 are no longer connected under the action of the pilot valve core of the hydraulic travel priority valve CT1. The right end of the cone valve core assembly of the hydraulic travel priority valve CT1 is pressurized, and the cone valve core of the hydraulic travel priority valve CT1 is closed under pressure. The working oil in the P1 main oil circuit can only enter the P1 parallel main oil circuit of the fully electric linear travel valve through the first throttling hole of the cone valve core of the hydraulic travel priority valve CT1.

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