Large excavator multi-way valve additionally provided with confluence logic valve

Abstract

The utility model relates to a hydraulic component, in particular to a large excavator multi-way valve additionally provided with a confluence logic valve, which is different from the prior art in that an oil outlet of a standby valve core is connected with an oil cylinder of a breaking hammer, and a second main pump oil way supplies oil to the oil cylinder of the breaking hammer; a confluence logic valve body is used for replacing the cover plate, a retaining valve and a two-position three-way pilot slide valve are installed in the confluence logic valve body, an oil inlet of the retaining valve is communicated with the standby oil port, and a first oil outlet of the retaining valve is connected with an oil outlet of the standby valve element; and a signal port of the pilot slide valve is connected with a signal inlet of the first bypass stop valve core. Compared with the prior art, through the control of the confluence logic valve, when the movable arm presses down to strike the hammer, the oil supply of the oil path is not cut off, so that the speed and the efficiency of the hammer are improved.

Description

Technical Field

[0001] The utility model relates to a hydraulic component, in particular to a large excavator multi-way valve with a converging logic valve added thereto. Background Art

[0002] The applicant previously disclosed a multi-way valve for large excavators in CN213448643U. The valve comprises three valve bodies (upper, middle, and lower), 12 main valve cores, a main relief valve, eight port relief valves, two locking valves, 0-3 logic valves, and several one-way valves. The upper valve body houses the straight-travel valve core, the left-travel valve core, the right-travel valve core, and the swing valve core. The middle valve body houses the boom 1 valve core, the boom 2 valve core, the bucket valve core, and a spare valve core. The lower valve body houses the arm 1 valve core, the arm 2 valve core, the first bypass shut-off valve core, and the second bypass shut-off valve core. This valve features dual-pump converging and flow regeneration functions, reducing fuel consumption and improving operating efficiency. However, when the excavator is using a breaker hammer, the spare valve core 13 is connected to the breaker hammer. However, when the boom is pressed down, the boom 1 valve core shifts to the right, reducing flow and potentially cutting off the fuel supply when the boom is pressed down to engage the hammer, slowing the hammering speed. Utility Model Content

[0003] In order to better achieve confluence and logic control, the utility model is based on the original multi-way valve for large excavators. When the spare valve core is activated, a confluence logic valve is added to control it, so as to avoid oil interruption when the boom is pressed down to hammer, and to increase the hammering speed. To this end, the technical solution adopted by the utility model is:

[0004] A multi-way valve for a large excavator equipped with a converging logic valve comprises a spare valve core, a first bypass cut-off valve core and a cover plate fixed to the lower valve body, wherein the cover plate blocks the spare oil port. Unlike the prior art, the oil outlet of the spare valve core is connected to the oil cylinder of the breaker hammer, and the second main pump oil circuit supplies oil to the oil cylinder of the breaker hammer; the cover plate is replaced by a converging logic valve body, in which a holding valve and a two-position three-way pilot slide valve are installed, the oil inlet of the holding valve is connected to the spare oil port, the first oil outlet of the holding valve is connected to the oil outlet of the spare valve core; the signal port of the pilot slide valve is connected to the signal inlet of the first bypass cut-off valve core.

[0005] Furthermore, when there is no signal input to the signal port of the pilot slide valve, the pilot slide valve will connect the oil inlet of the maintaining valve with the oil inlet behind the plug of the maintaining valve, so as to keep the pressure at both ends of the valve cavity equal, but the area of ​​the left end piston is larger than the area of ​​the right end plunger, so the plunger cuts off the connection between the oil inlet of the maintaining valve and the oil outlet of the maintaining valve, and the oil pressure of the first main pump oil circuit cannot be combined to the oil cylinder of the breaker hammer; when there is a signal input to the signal port of the pilot slide valve, the pilot slide valve will connect the second lateral oil port of the maintaining valve with the oil inlet behind the plug of the maintaining valve, so as to keep the pressure at both ends of the valve piston balanced, and the plunger moves left under the action of the oil pressure of the first main pump oil circuit provided by the spare oil port, and the oil outlet of the maintaining valve is connected to the oil inlet of the maintaining valve, so that the oil pressure of the first main pump oil circuit is combined to the oil cylinder of the breaker hammer.

[0006] Furthermore, the holding valve includes a spring, which is arranged in the holding valve and on the left side of the plunger to increase the pressure on the left side of the backup valve core.

[0007] Furthermore, the opening and closing of the backup valve core is controlled by adjusting the pressure of the spring to optimize the control accuracy and stability of the hydraulic system.

[0008] Furthermore, a one-way valve is connected in series to the oil path connecting the oil outlet of the holding valve and the oil outlet of the backup valve core, and the one-way valve cuts off the oil backflow from the oil outlet of the backup valve core to the oil outlet of the holding valve.

[0009] Furthermore, a solenoid valve is connected in series to the oil circuit connecting the signal port of the pilot slide valve and the signal inlet of the first bypass cut-off valve core, the oil inlet of the solenoid valve is connected to the backup oil port, and an induction switch is installed under the excavator arm, and the induction switch is connected to the solenoid valve.

[0010] Compared with the prior art, the present invention has the following beneficial technical effects:

[0011] 1. Increase hammering speed:

[0012] Through the control of the converging logic valve, it is ensured that the oil circuit will not be cut off when the boom is pressed down to hammer, thereby improving the speed and efficiency of hammering.

[0013] 2. Avoid flow reduction caused by throttling:

[0014] When the valve core of boom 1 moves to the right, the converging logic valve can ensure the stability of the oil flow, avoiding the flow reduction due to throttling, which affects the working performance of the breaker.

[0015] 3. Enhance the stability of the hydraulic system:

[0016] The use of the converging logic valve can dynamically adjust the oil circuit under different working conditions, thereby improving the stability and reliability of the entire hydraulic system.

[0017] 4. Optimize operating performance:

[0018] By precisely controlling the backup valve core, the operating performance of the excavator during crushing operations is improved, making the operation smoother and more responsive.

[0019] 5. Improve the flexibility and adaptability of the system:

[0020] The addition of the converging logic valve allows the multi-way valve to flexibly adjust the oil circuit according to different working requirements, thereby improving the adaptability of the system.

[0021] 6. Reduce energy loss:

[0022] Through reasonable oil circuit design, energy loss caused by pressure loss and improper flow control can be reduced, and energy utilization efficiency can be improved.

[0023] 7. Improve the intelligence level of the system:

[0024] If the converging logic valve contains intelligent control elements, the oil circuit can be automatically adjusted according to real-time feedback, thereby improving the intelligence level of the system.

[0025] 8. Enhance system security:

[0026] By rationally designing the oil circuit and control logic, oil circuit failures during high-load operation can be avoided, the risk of equipment damage can be reduced, and operational safety can be enhanced.

[0027] 9. Easy to maintain and adjust:

[0028] The design of the converging logic valve may allow for easier maintenance and adjustment, making it easier to adjust system parameters according to specific operating conditions.

[0029] 10. Improve work efficiency:

[0030] Taking the above effects into consideration, the utility model can improve the working efficiency of the excavator in crushing operations, shorten the operation cycle, and increase the operation output.

[0031] In short, the large excavator multi-way valve of the utility model can better meet the operating requirements under complex working conditions, especially when using a breaker hammer, and improve the operating capacity and economy of the excavator. BRIEF DESCRIPTION OF THE DRAWINGS

[0032] Figure 1 This is the overall hydraulic principle diagram of the original multi-way valve.

[0033] Figure 2 This is the overall hydraulic principle diagram of the utility model.

[0034] Numbers in the figure:

[0035] 1-upper valve body, 2-middle valve body, 3-lower valve body, 4-first main pump oil circuit, 5-second main pump oil circuit, 6-straight travel valve core, 7-right travel valve core, 8-left travel valve core, 9-rotation valve core, 10-boom 1 valve core, 11-boom 2 valve core, 12-bucket valve core, 13-spare valve core, 14-arm 2 valve core, 15-arm 1 valve core, 16-first bypass cut-off valve core, 17-second bypass cut-off valve core, 18-main relief valve, 19-port relief valve, 20-load holding valve, 21-rotation logic valve, 22-arm 1 logic valve, 23-bucket Rod 2 logic valve, 24-regeneration cut-off valve, 25'-cover plate, 25-merging logic valve body, 26-holding valve, 27-pilot slide valve, 28-breaking hammer, 29-check valve, 30-solenoid valve, P1-first main pump oil port, P2-second main pump oil port, P3-spare oil port, AO-oil outlet of spare valve core, AO1-first lateral oil port of holding valve, e-second lateral oil port of holding valve, XAO-signal port of pilot slide valve, XBP-signal inlet of first bypass cut-off valve core, DR-pressure relief port, d-oil inlet after plug, P-oil inlet of solenoid valve. DETAILED DESCRIPTION

[0036] The specific implementation methods of the present invention are further described in detail below in conjunction with the accompanying drawings. However, the following embodiments only list preferred embodiments, which only serve to explain and help understand the present invention and cannot be understood as limiting the present invention.

[0037] Embodiments of the present invention are described in detail below, examples of which are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements with the same or similar functions.

[0038] In this utility model, unless otherwise specified or limited, the terms "installed," "connected," "connect," "fixed," etc. should be understood in a broad sense. For example, they can refer to fixed connection, detachable connection, or integral connection; mechanical connection or electrical connection; direct connection or indirect connection through an intermediate medium; and internal communication between two components. Those skilled in the art will understand the specific meanings of the above terms in this utility model based on specific circumstances.

[0039] like Figure 2As shown, a multi-way valve for large excavators equipped with a converging logic valve includes a spare valve core 13, a first bypass cut-off valve core 16, and a cover plate 25' fixed to the lower valve body 3. The cover plate 25' blocks the spare oil port P3, and the oil outlet AO of the spare valve core is connected to the oil cylinder of the breaker hammer 28. The second main pump oil circuit 5 supplies oil to the oil cylinder of the breaker hammer 28. The cover plate 25' is replaced by a converging logic valve body 25. A holding valve 26 and a two-position three-way pilot slide valve 27 are installed in the converging logic valve body 25. The oil inlet RO1 of the holding valve is connected to the spare oil port P3, and the first lateral oil port AO1 of the holding valve is connected to the oil outlet AO of the spare valve core. The signal port XAO of the pilot slide valve is connected to the signal inlet XBP of the first bypass cut-off valve core. When there is no signal input to the signal port XAO of the pilot slide valve, the pilot slide valve 27 connects the oil inlet RO1 of the holding valve with the oil inlet d behind the plug of the holding valve, keeping the pressures at both ends of the valve cavity equal. However, the area of ​​the left-end piston is larger than that of the right-end plunger. Therefore, the plunger cuts off the connection between the oil inlet RO1 of the holding valve and the oil outlet AO1 of the holding valve, and the oil pressure of the first main pump oil circuit 4 cannot be combined to the oil cylinder of the breaker hammer 28. When there is a signal input to the signal port XAO of the pilot slide valve, the pilot slide valve 27 connects the second lateral oil port e of the holding valve with the oil inlet d behind the plug of the holding valve, keeping the pressures at both ends of the valve piston balanced. Under the action of the oil pressure of the first main pump oil circuit 4 provided by the backup oil port P3, the plunger moves left, and the oil outlet AO1 of the holding valve is connected to the oil inlet RO1 of the holding valve, so that the oil pressure of the first main pump oil circuit 4 is combined to the oil cylinder of the breaker hammer 28.

[0040] The control process of the multi-way valve of a large excavator equipped with a converging logic valve is as follows:

[0041] Initial state:

[0042] The cover plate 25 ′ is originally fixed on the lower valve body 3 to block the spare oil port P3 .

[0043] The oil outlet AO of the backup valve core 13 is directly connected to the oil cylinder of the breaker hammer 28 and is supplied with oil by the second main pump oil circuit 5 .

[0044] Control process:

[0045] 1. No signal input state:

[0046] The signal port XAO of the pilot spool valve 27 does not receive any signal.

[0047] The pilot spool valve 27 connects the oil inlet port RO1 of the holding valve 26 to the plug rear oil inlet port d.

[0048] Since the area on the left side of the piston is larger than the area on the right side of the plunger, the pressures at both ends of the valve cavity are kept equal, but the pressure on the left side is greater, causing the plunger to be cut off, preventing the oil inlet RO1 and the oil outlet AO1 of the valve from being connected.

[0049] Therefore, the oil pressure of the first main pump oil passage 4 cannot be combined with the oil cylinder of the breaker hammer 28 .

[0050] 2. Signal input status:

[0051] When the signal port XAO of the pilot spool valve 27 receives a signal, the pilot spool valve 27 changes the oil path.

[0052] The pilot spool valve 27 connects the second lateral oil port e of the holding valve 26 with the rear oil inlet port d.

[0053] 3. Maintain valve action:

[0054] Due to the conduction of the second lateral oil port e, the pressure at both ends of the piston of the valve 26 is kept balanced.

[0055] Under the action of the oil pressure provided by the spare oil port P3, the piston moves to the left.

[0056] 4. Oil pressure confluence:

[0057] The piston moves to the left, causing the oil outlet AO1 and the oil inlet RO1 of the valve to be connected.

[0058] The oil pressure of the first main pump oil circuit 4 is combined to flow into the oil cylinder of the breaker 28, thus realizing dual-pump oil supply.

[0059] 5.Breaker working:

[0060] The combined oil pressure increases the working pressure of the breaker hammer 28 cylinder and improves the crushing efficiency.

[0061] 6. System reset:

[0062] When the signal input stops, the pilot slide valve 27 is reset, cutting off the connection between the second lateral oil port e and the plug rear oil inlet port d, and returning to a no-signal input state.

[0063] 7. Technical effects:

[0064] By controlling the converging logic valve, the oil pressure of the first main pump oil circuit 4 is merged into the oil cylinder of the breaker 28 only when needed, thereby improving energy utilization efficiency and operation speed.

[0065] This avoids the situation where the oil circuit is cut off when the boom is pressed down to hammer, ensuring the continuous and stable operation of the breaker.

[0066] Technical advantages:

[0067] Flexibility: The confluence and separation of the oil circuits can be flexibly controlled according to work needs.

[0068] Efficiency: It improves the oil pressure supply when the breaker hammer is working and enhances the hammering efficiency.

[0069] Control accuracy: The precise control of the pilot slide valve 27 ensures the timeliness and accuracy of oil circuit switching.

[0070] Intelligence: The entire system can automatically adjust according to the working status, reducing manual intervention and improving the level of intelligence.

[0071] In another preferred embodiment, the holding valve 26 includes a spring positioned within the holding valve 26, to the left of the plunger, to increase pressure on the left side of the backup valve spool 13. By adjusting the spring pressure, the opening and closing of the backup valve spool 13 are controlled to optimize the control accuracy and stability of the hydraulic system. This spring is used to increase pressure on the left side of the plunger when there is no signal input or when the signal input varies. When there is no signal input to the signal port XAO of the pilot spool 27, the pilot spool 27 connects the rear oil passage HO with the front oil passage QO. The spring acts on the left side of the plunger in the holding valve 26, balancing the pressure on the right side of the plunger created by the connection between the rear oil passage HO and the front oil passage QO, thereby increasing pressure on the left side of the plunger. When a signal is received at the signal port XAO, the pilot spool 27 switches state, connecting the rear oil passage HO to the pressure relief port DR, relieving pressure on the left side of the plunger. After the plunger is relieved of pressure, the spring assists the plunger in quickly responding to pressure changes. By regulating the spring pressure, the opening and closing of the backup valve spool 13 can be more precisely controlled. The addition of a spring makes the control of holding valve 26 more sensitive and precise. By adjusting the spring's stiffness or pre-compression, the opening speed and force of the backup valve spool 13 can be adjusted. Spring-assisted pressure regulation helps reduce the impact of hydraulic oil pressure fluctuations on the control of the backup valve spool 13, improving the stability of the entire hydraulic system.

[0072] In another preferred embodiment, a one-way valve 29 is connected in series on the oil circuit connecting the oil outlet AO1 of the holding valve and the oil outlet AO of the backup valve core, and the one-way valve 29 cuts off the backflow from the oil outlet AO of the backup valve core to the oil outlet AO1 of the holding valve. When the oil outlet AO of the backup valve core 13 needs to be closed or the system pressure is reduced, the one-way valve 29 prevents the oil from flowing back from the oil outlet AO of the backup valve core to the oil outlet AO1 of the holding valve, ensuring the one-way flow of the oil circuit. The use of the one-way valve 29 improves the stability of the system and prevents pressure fluctuations or system instability caused by oil backflow. As a safety device, the one-way valve 29 can avoid hydraulic shock or equipment damage that may be caused by oil backflow when the backup valve core 13 is closed. By ensuring the one-way flow of oil, the one-way valve 29 helps to reduce energy loss caused by oil backflow and improve the energy-saving effect of the system.

[0073] In another preferred embodiment, a solenoid valve 30 is connected in series to the oil confluence between the signal port XAO of the pilot spool and the signal inlet XBP of the first bypass shut-off valve core. The oil inlet P of the solenoid valve is connected to the backup oil port P3. A sensing switch is installed under the excavator boom and is connected to the solenoid valve 30. When the excavator boom is lowered, the sensing switch sends an electrical signal to the solenoid valve 30. The solenoid valve 30 sends a signal to the signal port XAO of the pilot spool, and the backup oil port P3 is merged to the oil cylinder in the breaker hammer 28. At the same time, the solenoid valve 30 sends a signal to the signal inlet XBP of the first bypass shut-off valve core. When the oil cylinder in the breaker hammer 28 is independently actuated, the first bypass shut-off valve core 16 cuts off the passage of the first main pump oil port P1 pumping back to the oil tank, allowing the high-pressure oil in the first main pump oil port P1 to flow to the oil cylinder in the breaker hammer 28 through the one-way valve, thereby realizing a dual-pump confluence function in which the first main pump oil port P1 and the second main pump oil port P2 pumps simultaneously supply oil when the oil cylinder in the breaker hammer 28 is independently actuated. When the excavator's boom lowers, a sensor switch is triggered, sending an electrical signal to the solenoid valve 30. Upon receiving the signal from the sensor switch, the solenoid valve 30 activates, connecting its oil inlet P to the backup oil port P3. This activation of the solenoid valve 30 allows the oil in the backup oil port P3 to merge with the cylinders within the hammer 28, providing additional oil supply. Simultaneously, the solenoid valve 30 sends a signal to the signal inlet XBP of the first bypass shut-off valve spool 16, activating the first bypass shut-off valve spool 16. When the cylinders within the hammer 28 need to operate independently, the first bypass shut-off valve spool 16 shuts off the flow from the first main pump port P1 back to the tank. With this shut-off, the high-pressure oil in the first main pump port P1 flows through the check valve to the cylinders within the hammer 28. The coordinated operation of the solenoid valve 30 and the first bypass shut-off valve spool 16 enables dual-pump merging, allowing the first and second main pump ports P1 and P2 to simultaneously supply oil when the cylinders within the hammer 28 operate independently, improving the operating efficiency and power of the cylinders. The entire control process is automatically triggered by an inductive switch, achieving intelligent control, reducing the need for manual operation and improving operational safety and efficiency. Precisely controlling the oil supply prevents unnecessary oil flow, reduces energy loss, and enhances the system's energy efficiency. The inclusion of solenoid valve 30 enables the system to automatically adjust the oil circuit based on the actual movement of the excavator's boom, enhancing its adaptability and flexibility.

[0074] Although the embodiments of the present invention have been shown and described above, it can be understood that the above embodiments are illustrative and cannot be understood as limiting the present invention. Ordinary technicians in this field can change, modify, replace and modify the above embodiments within the scope of the present invention without departing from the principles and purpose of the present invention. Simple combination changes are included in the protection of the present invention.

Claims

1. A multi-way valve for a large excavator equipped with a converging logic valve, comprising a spare valve core (13), a first bypass cut-off valve core (16), and a cover plate (25') fixed to a lower valve body (3), wherein the cover plate (25') blocks a spare oil port (P3), and is characterized in that: The oil outlet (AO) of the spare valve core is connected to the oil cylinder of the breaker hammer (28), and the second main pump oil circuit (5) supplies oil to the oil cylinder of the breaker hammer (28); the cover plate (25') is replaced by a converging logic valve body (25), and a holding valve (26) and a two-position three-way pilot slide valve (27) are installed in the converging logic valve body (25); the oil inlet (RO1) of the holding valve is connected to the spare oil port (P3), and the first lateral oil port (AO1) of the holding valve is connected to the oil outlet (AO) of the spare valve core; the signal port (XAO) of the pilot slide valve is connected to the signal inlet (XBP) of the first bypass cut-off valve core.

2. A large excavator multi-way valve equipped with a converging logic valve according to claim 1, characterized in that: When there is no signal input to the signal port (XAO) of the pilot slide valve, the pilot slide valve (27) connects the oil inlet (RO1) of the holding valve with the oil inlet (d) behind the plug of the holding valve, keeping the pressure at both ends of the valve cavity equal. However, the area of ​​the left end piston is larger than that of the right end plunger, so the plunger cuts off the connection between the oil inlet (RO1) of the holding valve and the oil outlet (AO1) of the holding valve, and the oil pressure of the first main pump oil circuit (4) cannot be combined to the oil cylinder of the breaker (28); When a signal is input to the signal port (XAO) of the slide valve, the pilot slide valve (27) connects the second lateral oil port (e) of the holding valve with the oil inlet (d) behind the plug of the holding valve, and balances the pressure at both ends of the piston of the holding valve. Under the action of the oil pressure of the first main pump oil circuit (4) provided by the spare oil port (P3), the plunger moves left, and the oil outlet (AO1) of the holding valve is connected with the oil inlet (RO1) of the holding valve, and the oil pressure of the first main pump oil circuit (4) is combined to the oil cylinder of the breaker (28).

3. A large excavator multi-way valve equipped with a converging logic valve according to claim 1, characterized in that: The holding valve (26) includes a spring, which is arranged in the holding valve (26) and on the left side of the plunger, and is used to increase the pressure on the left side of the backup valve core (13).

4. A large excavator multi-way valve equipped with a converging logic valve according to claim 3, characterized in that: The opening and closing of the backup valve core (13) is controlled by adjusting the pressure of the spring to optimize the control accuracy and stability of the hydraulic system.

5. A large excavator multi-way valve equipped with a converging logic valve according to claim 1, characterized in that: A one-way valve (29) is connected in series to the oil path connecting the oil outlet (AO1) of the holding valve and the oil outlet (AO) of the backup valve core. The one-way valve (29) cuts off backflow from the oil outlet (AO) of the backup valve core to the oil outlet (AO1) of the holding valve.

6. A large excavator multi-way valve equipped with a converging logic valve according to claim 1, characterized in that: A solenoid valve (30) is connected in series to the oil circuit connecting the signal port (XAO) of the pilot slide valve and the signal inlet (XBP) of the first bypass cut-off valve core, the oil inlet (P) of the solenoid valve is connected to the standby oil port (P3), and an induction switch is installed below the excavator boom, the induction switch being connected to the solenoid valve (30).

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