Work machine control system and work machine

Abstract

This disclosure relates to a control system for construction machinery and the construction machinery itself. The control system includes: a load-sensitive valve group connected to a pump body to regulate the pressure and / or flow rate output by the pump body; a multi-way valve group for the upper structure connected to the pump body and the load-sensitive valve group; a hydraulic output port connected to the pump body and the hydraulic output port; a first switching valve group disposed between the load-sensitive valve group and the upper structure multi-way valve group, and between the load-sensitive valve group and the hydraulic output port, configured to selectively open the oil passage between the load-sensitive valve group and the upper structure multi-way valve group or between the load-sensitive valve group and the hydraulic output port; and a processor configured to open the oil passage between the load-sensitive valve group and the upper structure multi-way valve group under upper structure operation, and to open the oil passage between the load-sensitive valve group and the hydraulic output port under hydraulic output. This system can achieve high pump output power and high output pressure without affecting the excavation operation of the upper structure.

Description

Technical Field

[0001] This disclosure relates to the field of construction machinery, and more particularly to a construction machinery control system and construction machinery. Background Technology

[0002] Excavators are one of the core pieces of equipment in emergency rescue missions such as road repair, obstacle removal, and tunnel hazard mitigation. In these missions, excavators are required not only to be equipped with buckets, hydraulic breakers, grippers, hydraulic shears, rock drills, and other implements, but also to provide power and hydraulic power outputs. This serves as a mobile power source for rescue personnel's manual tools or to provide hydraulic power and electricity to other rescue equipment. Excavators require manual operation of the boom from the cab. Quick-connect couplings are located at the boom end, which can serve as hydraulic interfaces for hydraulic breakers, grippers, hydraulic shears, rock drills, etc., or as standalone hydraulic output ports.

[0003] In related technologies, the hydraulic ports of excavators are output through load-sensitive pumps and load-sensitive multi-way valves. Generally, the overflow pressure of load-sensitive multi-way valves is below 30MPa, while the output pressure of commonly used load-sensitive piston pumps is above 30MPa. However, the valve stem pressure drop in the load-sensitive valve is about 2MPa, which makes the hydraulic pressure output from this port lower than the output pressure of the piston pump. Consequently, the hydraulic power output from this port is lower than the rated power of the piston pump, affecting operation. Summary of the Invention

[0004] In view of this, the present disclosure provides a control system for engineering machinery and engineering machinery that helps to improve output power.

[0005] In one aspect of this disclosure, a control system for construction machinery is provided, comprising:

[0006] tank;

[0007] Pump body, connected to oil tank;

[0008] The power source is connected to the pump body.

[0009] A load-sensitive valve assembly is connected to the pump body to regulate the pressure and / or flow rate output by the pump body;

[0010] The upper multi-way valve assembly is connected to the pump body and the load-sensitive valve assembly;

[0011] Hydraulic output port, connected to the pump body and hydraulic output port, is used for connection to operating machinery;

[0012] The first switching valve assembly, located in the oil passage between the load-sensitive valve assembly and the upper vehicle multi-way valve assembly, and in the oil passage between the load-sensitive valve assembly and the hydraulic output port, is configured to selectively connect either the oil passage between the load-sensitive valve assembly and the upper vehicle multi-way valve assembly or the oil passage between the load-sensitive valve assembly and the hydraulic output port; and

[0013] The processor is signal-connected to the first switching valve group;

[0014] The construction machinery has an on-board operation state and a hydraulic output state. The processor is configured to connect the oil circuit between the load-sensitive valve group and the on-board multi-way valve group when the on-board operation state is in operation state, and to connect the oil circuit between the load-sensitive valve group and the hydraulic output port when the hydraulic output state is in operation state.

[0015] In some embodiments, the engineering machinery control system further includes:

[0016] The second switching valve group, located in the oil passage between the pump body and the upper vehicle multi-way valve group, is configured to open or close the oil passage between the pump body and the upper vehicle multi-way valve group.

[0017] The processor is signal-connected to the second switching valve group and is configured to open the oil circuit between the pump body and the upper vehicle multi-way valve group when the upper vehicle is in operation state, and to close the oil circuit between the pump body and the upper vehicle multi-way valve group when the hydraulic output state is in operation state.

[0018] In some embodiments, the hydraulic output port includes a quick-change interface configured to cut off pressurized oil from the pump body when the vehicle is in an on-board working state.

[0019] In some embodiments, the engineering machinery control system further includes:

[0020] The central rotary joint is located in the oil circuit between the pump body and the upper multi-way valve group, and has a load feedback oil port;

[0021] The first switching valve group includes a first switching valve and a second switching valve. The first switching valve is located in the oil circuit between the load feedback port of the central rotary joint and the load-sensitive valve group, and the second switching valve is located in the oil circuit between the hydraulic output port and the load-sensitive valve group.

[0022] In some embodiments, the first switching valve has two operating positions. When the first switching valve is in the first operating position, it opens the oil passage between the load feedback port of the central rotary joint and the load-sensitive valve group, and when it is in the second operating position, it closes the oil passage between the load feedback port of the central rotary joint and the load-sensitive valve group.

[0023] The second switching valve has two working positions. When it is in the first working position, the second switching valve is configured to cut off the oil passage between the hydraulic output port and the load-sensitive valve group, and when it is in the second working position, it opens the oil passage between the hydraulic output port and the load-sensitive valve group.

[0024] The processor is signal-connected to the first and second switching valves. The processor is configured to keep the first and second switching valves in a first working position when the vehicle is in operation, and to keep the first and second switching valves in a second working position when the hydraulic output is in operation.

[0025] In some embodiments, the central rotary joint has an oil inlet;

[0026] The second switching valve group includes:

[0027] A hydraulically controlled check valve connects to the oil inlet of the pump body and the central rotary joint; and

[0028] A directional control valve, connected to a pilot-operated check valve, is configured to switch the pressure input state of the pilot-operated check valve so that the pilot-operated check valve adjusts the direction of the permissible oil passage.

[0029] In some embodiments, the directional valve has two operating positions. When the directional valve is in the first operating position, it connects the oil passage between the hydraulic check valve and the oil tank so that the hydraulic check valve can be opened from the pump body to the upper multi-way valve group. When the directional valve is in the second operating position, it connects the oil passage between the pump body and the hydraulic check valve so that the hydraulic check valve can be closed from the pump body to the upper multi-way valve group.

[0030] The processor is configured to put the directional valve in the first working position when it is in the on-board operation state, and to put the directional valve in the second working position when it is in the hydraulic output state.

[0031] In some embodiments, the spool flow rate of the pilot-operated check valve is greater than that of the spool flow rate of the directional control valve.

[0032] In another aspect of this disclosure, an engineering machine is provided, comprising:

[0033] Such as any of the above-mentioned engineering machinery control systems;

[0034] The loading mechanism is configured to connect to the loading multi-way valve group;

[0035] The operating machinery is configured to connect to the hydraulic output port.

[0036] In some embodiments, the loading mechanism includes an excavating arm.

[0037] Therefore, according to the embodiments of this disclosure, by setting a first switching valve group, the load-sensitive valve group can be selectively connected to the upper vehicle multi-way valve group or the hydraulic output port in the upper vehicle operation state and the hydraulic output state, respectively. This avoids the output pressure provided by the pump body being affected by the load feedback of the upper vehicle multi-way valve when the hydraulic output port is connected to the load, so that the hydraulic output port can provide full pressure to the load and realize the full power output of the pump body. This helps to provide greater hydraulic output power for rescue tools in emergency rescue and other working conditions, and improves the safety and reliability of rescue work. Attached Figure Description

[0038] The accompanying drawings, which form part of this specification, illustrate embodiments of this disclosure and, together with the specification, serve to explain the principles of this disclosure.

[0039] This disclosure will become clearer with reference to the accompanying drawings and the following detailed description, wherein:

[0040] Figure 1 These are schematic diagrams of structures based on some embodiments of the engineering machinery control system disclosed herein;

[0041] Figure 2 This is a connection diagram based on some embodiments of the engineering machinery control system disclosed herein;

[0042] Figure 3 These are schematic diagrams of some embodiments of the first switching valve group of the engineering machinery control system according to the present disclosure;

[0043] Figure 4 This is a schematic diagram of the structure of some embodiments of the second switching valve group of the engineering machinery control system according to the present disclosure;

[0044] In the picture:

[0045] 11. Oil tank; 12. Pump body; 13. Power source; 14. Radiator; 15. Air filter; 2. Load-sensitive valve assembly; 3. Upper vehicle multi-way valve assembly; 31. Oil inlet coupling; 32. Boom coupling; 33. Stick coupling; 34. Bucket coupling; 35. Swing motor coupling; 36. Tail coupling; 4. Hydraulic output port; 41. High-pressure hydraulic output port; 42. Hydraulic output return port; 5. First switching valve assembly; 51. First switching valve; 52. Second switching valve; 6. Processor; 7. Second switching valve assembly; 71. Hydraulic control check valve; 72. Directional valve; 81. Load feedback port; 82. Oil inlet port; 83. Oil drain port; 91. Boom cylinder; 92. Stick cylinder; 93. Bucket cylinder; 94. Swing motor.

[0046] It should be understood that the dimensions of the various parts shown in the accompanying drawings are not drawn to actual scale. Furthermore, the same or similar reference numerals denote the same or similar components. Detailed Implementation

[0047] Various exemplary embodiments of the present disclosure will now be described in detail with reference to the accompanying drawings. The descriptions of the exemplary embodiments are merely illustrative and are in no way intended to limit the present disclosure or its application or use. The present disclosure may be implemented in many different forms and is not limited to the embodiments described herein. These embodiments are provided so that the present disclosure will be thorough and complete, and will fully express the scope of the disclosure to those skilled in the art. It should be noted that, unless specifically stated otherwise, the relative arrangement of components and steps, the composition of materials, numerical expressions, and values ​​set forth in these embodiments should be interpreted as exemplary only and not as limiting.

[0048] The terms "first," "second," and similar words used in this disclosure do not indicate any order, quantity, or importance, but are merely used to distinguish different parts. Words such as "including" or "contains" mean that the element preceding the word encompasses the element listed after it, and do not exclude the possibility of encompassing other elements as well. Terms such as "above," "below," "left," and "right" are used only to indicate relative positional relationships; when the absolute position of the described object changes, this relative positional relationship may also change accordingly.

[0049] In this disclosure, when a specific device is described as being located between a first device and a second device, an intermediary device may or may not be present between the specific device and the first or second device. When a specific device is described as being connected to other devices, the specific device may be directly connected to the other devices without an intermediary device, or it may be not directly connected to the other devices but have an intermediary device.

[0050] All terms used in this disclosure (including technical or scientific terms) have the same meaning as understood by one of ordinary skill in the art to which this disclosure pertains, unless otherwise specifically defined. It should also be understood that terms defined in a general dictionary, such as a dictionary, should be interpreted as having a meaning consistent with their meaning in the context of the relevant art, and not as having an idealized or highly formalized meaning, unless expressly defined herein.

[0051] Techniques, methods, and equipment known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and equipment should be considered part of the specification.

[0052] Excavators are one of the core pieces of equipment in emergency rescue missions such as road repair, obstacle removal, and tunnel hazard mitigation. In these missions, excavators are required not only to be equipped with buckets, hydraulic breakers, grippers, hydraulic shears, rock drills, and other implements, but also to provide power and hydraulic power outputs. This serves as a mobile power source for rescue personnel's manual tools or to provide hydraulic power and electricity to other rescue equipment. Excavators require manual operation of the boom from the cab. Quick-connect couplings are located at the boom end, which can serve as hydraulic interfaces for hydraulic breakers, grippers, hydraulic shears, rock drills, etc., or as standalone hydraulic output ports.

[0053] In related technologies, the hydraulic ports of excavators output pressure through load-sensitive pumps and load-sensitive multi-way valves. Generally, the overflow pressure of load-sensitive multi-way valves is below 30MPa, while the output pressure of commonly used load-sensitive piston pumps is above 30MPa. However, the valve stem pressure drop in the load-sensitive valve is about 2MPa, which makes the hydraulic pressure output from this port lower than the output pressure of the piston pump. Consequently, the hydraulic power output from this port is lower than the rated power of the piston pump, making it impossible to achieve the full power output of the piston pump. This affects the excavator's operation, and manually operating the excavator arm at emergency rescue sites poses a certain degree of danger.

[0054] In view of this, in one aspect of the present disclosure, a control system for engineering machinery is provided, which helps to improve output power.

[0055] Figure 1 These are schematic diagrams of structures based on some embodiments of the engineering machinery control system disclosed herein. Figure 2 This is a connection diagram based on some embodiments of the engineering machinery control system disclosed herein, with reference to... Figure 1 and Figure 2 The control system for construction machinery includes an oil tank 11, a pump body 12, a power source 13, a load-sensitive valve group 2, an upper multi-way valve group 3, a hydraulic output port 4, and a first switching valve group 5. Construction machinery includes, but is not limited to, excavators and other emergency rescue vehicles.

[0056] The pump body 12 is connected to the oil tank 11, and the power source 13 is connected to the pump body 12. The power source 13 includes, but is not limited to, an engine or an electric motor. The engineering machinery control system may also include a radiator 14 and an air filter 15. The radiator 14 is driven by an electric motor, and the air filter 15 is connected to the oil tank 11.

[0057] The load-sensitive valve assembly 2 is connected to the pump body 12, which is a load-sensitive plunger pump with functions such as load sensing, pressure cut-off, and constant power control. The load-sensitive valve assembly 2 can adjust the pressure and / or flow rate output by the pump body 12. The upper multi-way valve assembly 3 is connected to the pump body 12 and the load-sensitive valve assembly 2.

[0058] The hydraulic output port 4 is connected to the pump body 12 and the oil tank 11 for connection with the working machinery. The hydraulic output port 4 includes a hydraulic output high pressure port 41 and a hydraulic output return port 42. Both the hydraulic output high pressure port 41 and the hydraulic output return port 42 can be quick-change connectors or plugs. The two ports of the hydraulic output port 4 are fixed to the vehicle frame through the wall-mounted connector.

[0059] Hydraulic output port 4 can connect to various work machines to provide hydraulic power, enabling a wide range of operational functions. Work machines include, but are not limited to, rescue equipment equipped with buckets, breakers, grippers, hydraulic shears, rock drills, and other implements, as well as manual tools for rescue personnel that require hydraulic power.

[0060] The first switching valve group 5 is located in the oil circuit between the load-sensitive valve group 2 and the upper vehicle multi-way valve group 3, and in the oil circuit between the load-sensitive valve group 2 and the hydraulic output port 4. It is configured to selectively connect either the oil circuit between the load-sensitive valve group 2 and the upper vehicle multi-way valve group 3 or the oil circuit between the load-sensitive valve group 2 and the hydraulic output port 4.

[0061] Construction machinery has an on-board operation state and a hydraulic output state. In the on-board operation state, the construction machinery is in operation and can carry out excavation and other operations. In the hydraulic output state, the hydraulic output port 4 of the construction machinery supplies power to other construction machinery, which can carry out crushing, shearing, clamping and other operations.

[0062] The processor 6 is signal-connected to the first switching valve group 5. The processor 6 is configured to, in the on-vehicle operation state, open the oil circuit between the first switching valve group 5 and the load-sensitive valve group 2 and the on-vehicle multi-way valve group 3 to provide load feedback for on-vehicle operation and adjust the output pressure and flow of the pump body 12 in real time; in the hydraulic output state, open the oil circuit between the first switching valve group 5 and the hydraulic output port 4 to provide load feedback for other operations and realize the full pressure and full power output of the pump body 12.

[0063] In this embodiment, by setting the first switching valve group 5, the load-sensitive valve group 2 is selectively connected to the upper vehicle multi-way valve group 3 or the hydraulic output port 4 in the upper vehicle operation state and the hydraulic output state, respectively. This avoids the output pressure provided by the pump body 12 being affected by the load feedback of the upper vehicle multi-way valve group 3 when the hydraulic output port 4 is connected to the load, so that the hydraulic output port 4 can provide full pressure to the load and realize the full power output of the pump body 12. This helps to provide greater hydraulic output power for rescue tools in emergency rescue and other working conditions, and improves the safety and reliability of rescue work.

[0064] refer to Figure 1In some embodiments, the engineering machinery control system further includes a second switching valve group 7, which is disposed in the oil passage between the pump body 12 and the upper vehicle multi-way valve group 3, and is configured to open or close the oil passage between the pump body 12 and the upper vehicle multi-way valve group 3.

[0065] The processor 6 is signal-connected to the second switching valve group 7 and is configured to open the oil passage between the pump body 12 and the upper vehicle multi-way valve group 3 when the upper vehicle is in operation mode, and to close the oil passage between the pump body 12 and the upper vehicle multi-way valve group 3 when the hydraulic output mode is in operation mode.

[0066] In this embodiment, by setting a second switching valve group 7, the pump body 12 supplies oil to the upper multi-way valve group 3 in the upper vehicle operation state, while in the hydraulic output state, the hydraulic oil output from the pump body 12 to the upper multi-way valve group 3 is cut off. This allows the pump body 12 to supply oil to the upper multi-way valve group 3 and the hydraulic output port 4 respectively in the upper vehicle operation state and the hydraulic output state, without affecting each other's required hydraulic flow, thereby improving the reliability and stability of upper vehicle operation and load operation.

[0067] In some embodiments, the hydraulic output port 4 includes a quick-change interface or a plug. The two ports of the hydraulic output port 4 are fixed to the frame via a through-wall connector. The quick-change interface or plug is configured to cut off the pressurized oil from the pump body 12 during on-vehicle operation, ensuring no flow diversion to the on-vehicle's required flow. In this embodiment, the hydraulic output port can cut off the pressurized oil from the pump body 12 during on-vehicle operation, thereby ensuring the pressure and power output of the pump body 12 during on-vehicle operation and enabling the on-vehicle to achieve better operating conditions.

[0068] Figure 3 This is a structural schematic diagram of some embodiments of the first switching valve group of the engineering machinery control system according to the present disclosure, with reference to... Figure 1 and Figure 3 In some embodiments, the construction machinery also includes a central rotary joint, which is located in the oil passage between the pump body 12 and the upper multi-way valve group 3, and has a load feedback oil port 81. The central rotary joint may include multiple oil ports and several wiring harnesses. The load feedback oil port 81 may include two oil ports, which are respectively connected to the pump body 12 and the upper multi-way valve group 3. The wiring harness can provide low-voltage power to the valve core of the upper multi-way valve group 3.

[0069] The first switching valve group 5 includes a first switching valve 51 and a second switching valve 52. The first switching valve 51 is located in the oil circuit between the load feedback port 81 of the central rotary joint and the load sensitive valve group 2, and the second switching valve 52 is located in the oil circuit between the hydraulic output port 4 and the load sensitive valve group 2.

[0070] In this embodiment, the first switching valve group 5 includes two switching valves, which respectively switch the connection between the load feedback oil port 81 and the load sensitive valve group 2 and between the hydraulic output port 4 and the load sensitive valve group 2.

[0071] refer to Figure 1 and Figure 3 In some embodiments, the first switching valve 51 is a two-position two-normally-open switching valve. The first switching valve 51 has two working positions. When the first working position is in the first working position, the first switching valve 51 opens the oil passage between the load feedback port 81 of the central rotary joint and the load sensitive valve group 2. When the second working position is in the second working position, the oil passage between the load feedback port 81 of the central rotary joint and the load sensitive valve group 2 is closed.

[0072] The second switching valve 52 is a two-position normally closed switching valve. The second switching valve 52 has two working positions. When the second switching valve 52 is in the first working position, it cuts off the oil passage between the hydraulic output port 4 and the load-sensitive valve group 2. When it is in the second working position, it opens the oil passage between the hydraulic output port 4 and the load-sensitive valve group 2.

[0073] The processor 6 is signal-connected to the first switching valve 51 and the second switching valve 52. The processor 6 is configured to put the first switching valve 51 and the second switching valve 52 in a first working position when the machine is in operation, and to put the first switching valve 51 and the second switching valve 52 in a second working position when the hydraulic output is in operation.

[0074] When the pump is in operation, the power source 13 starts after the high voltage is turned on, which drives the pump body 12 to a low-pressure standby state. The first switch valve 51 and the second switch valve 52 are not energized. That is, the first switch valve 51 opens the oil circuit between the load feedback port 81 of the central rotary joint and the load sensitive valve group 2, and the second switch valve 52 closes the oil circuit between the hydraulic output port 4 and the load sensitive valve group 2. The load pressure fed back from the multi-way valve group 3 of the pump body is fed back to the load sensitive valve group 2 of the pump body 12 through the load feedback port 81 of the central rotary joint and the first switch valve 51, so as to adjust the output pressure and flow of the pump body 12 in real time.

[0075] In hydraulic output mode, after high-pressure power is applied, the motor or engine starts, driving the pump body 12 to a low-pressure standby state, and the pump body 12 outputs a large displacement. The first switch valve 51 and the second switch valve 52 are both energized, that is, the first switch valve 51 cuts off the oil circuit between the load feedback oil port 81 of the central rotary joint and the load sensitive valve group 2, preventing the feedback oil circuit from overflowing through the upper multi-way valve group 3, and the second switch valve 52 opens the oil circuit between the hydraulic output port 4 and the load sensitive valve group 2, and the load sensitive valve group 2 works under the action of spring force.

[0076] Before the pump body 12 reaches the constant power setting value, as the pressure increases, the hydraulic oil output by the pump body 12 enters the load-sensitive valve group 2. The load-sensitive valve group 2 is connected to the external load connected to the hydraulic output port 4. The output pressure of the pump body 12 and the output pressure of the load-sensitive valve group 2 form a stable pressure difference, ensuring the constant flow output of the pump body 12.

[0077] When the pump body 12 reaches the set constant power value, the pump displacement of the pump body 12 begins to decrease as the pressure continues to increase.

[0078] Before the pump body 12 reaches the set pressure of the pressure compensation valve, the pump body 12 can output a stable pressure. The maximum value of this pressure is the pressure cut-off adjustment value p of the pump body 12. At this time, the output flow rate of the pump body 12 is the maximum output flow rate Q of the pump body 12. Therefore, the output power of the pump body 12 is P. max =p × Q ÷ 60, which is the maximum output power of pump body 12, where the pressure p is in MPa, the flow rate Q is in L / min, and the power P is in kW. In this state, pump body 12 is equivalent to a fixed displacement pump, outputting a maximum stable pressure p and a maximum stable power Q. max It can provide stable hydraulic driving force for external equipment.

[0079] When the pressure rises to the set pressure of the pressure compensation valve, the valve operates in the left position, and the load-sensitive valve and the constant power valve lose their function. The pressure oil is led to the variable cylinder through the pressure compensation valve, so that the displacement of the pump body 12 is reduced to the minimum. At this time, the output flow of the pump body 12 can only meet the internal leakage. Under this working condition, the output pressure of the pump body 12 is the set pressure of the pressure compensation valve, and the flow is almost 0, reaching the high-pressure standby working condition of the pump body 12.

[0080] As the load on the external equipment increases, the output pressure of pump body 12 gradually increases, while the output flow rate initially remains stable before gradually decreasing to almost zero. The output power of pump body 12 initially increases, then gradually decreases, finally reaching zero. Adjusting the load on the external equipment allows us to obtain the maximum output power point of pump body 12. The output pressure corresponding to this maximum output power point is p, and the corresponding output flow rate is Q. The maximum output power P of pump body 12 is then calculated. max .

[0081] In this embodiment, the output pressure and flow rate of the pump body 12 change in real time with the load of the external equipment at the hydraulic output port under hydraulic output state, so that the output power of the pump body 12 also changes in real time with the load of the external equipment. Adjusting the load of the external equipment can enable the pump body 12 to output maximum power and provide a stable hydraulic driving force for the external equipment.

[0082] Figure 4 This is a schematic diagram of the structure of some embodiments of the second switching valve group of the engineering machinery control system according to the present disclosure, with reference to... Figure 1 and Figure 4 In some embodiments, the central rotary joint has an oil inlet 82.

[0083] The second switching valve group 7 includes a hydraulic control check valve 71 and a reversing valve 72. The hydraulic control check valve 71 is connected to the pump body 12 and the oil inlet 82 of the central rotary joint. The upper multi-way valve group 3 receives oil from the pump body 12 through the oil inlet 82 of the central rotary joint.

[0084] The reversing valve 72 is connected to the hydraulic control check valve 71. The reversing valve 72 is configured to switch the pressure input state of the hydraulic control check valve 71 so that the hydraulic control check valve 71 can open or close the oil passage between the pump body 12 and the oil inlet 82 of the central rotary joint.

[0085] In this embodiment, the second switching valve group 7 can take the form of a hydraulic control check valve 71 and a reversing valve 72. The pressure input state of the hydraulic control check valve 71 is switched by the reversing valve 72, thereby adjusting the conduction direction of the hydraulic control check valve 71.

[0086] refer to Figure 1 and Figure 4 In some embodiments, the reversing valve 72 has two operating positions. When the reversing valve 72 is in the first operating position, it connects the oil passage between the hydraulic control check valve 71 and the oil tank 11 so that the hydraulic control check valve 71 is opened from the pump body 12 to the upper multi-way valve group 3. When the reversing valve 72 is in the second operating position, it connects the hydraulic control oil passage between the pump body 12 and the hydraulic control check valve 71 so that the hydraulic control check valve 71 is closed from the pump body 12 to the upper multi-way valve group 3.

[0087] The reversing valve 72 is a two-position three-way reversing valve. The processor 6 is configured to keep the reversing valve 72 in the first working position when the vehicle is in operation. The reversing valve 72 must not be in the left position. The hydraulic port in the hydraulic control check valve 71 discharges oil through the left position of the reversing valve 72. The pressure oil output by the pump body 12 overcomes the spring force of the hydraulic control check valve 71, and the hydraulic control check valve 71 opens. The pressure oil output by the pump body 12 flows into the vehicle multi-way valve group 3 after passing through the hydraulic control check valve 71 and the oil inlet 82.

[0088] The processor 6 is configured to put the directional valve 72 in the second working position when the hydraulic output state is in the hydraulic output state. The directional valve 72 is energized and in the right position. The pressure oil from the pump body 12 is connected to the hydraulic control oil circuit of the hydraulic control check valve 71, thereby putting the hydraulic control check valve 71 in the locked state. The hydraulic oil output by the pump body 12 is cut off by the hydraulic control check valve 71. The hydraulic oil output by the pump body 12 drives the external hydraulic equipment through the hydraulic output port 4.

[0089] In this embodiment, the working position of the reversing valve 72 is switched to adjust the oil circuit direction allowed by the hydraulic control check valve 71, so that the pump body 12 can supply oil to the multi-way valve group 3 of the upper vehicle in the upper vehicle operation state, and supply oil to the external hydraulic equipment in the hydraulic output state. The oil supply of the pump body 12 is not diverted in each state, reducing the pressure loss of the pump body 12 when working on the upper vehicle, and realizing the full power output of the pump body 12 when hydraulically outputting, so that the upper vehicle operation and the operation of the external hydraulic equipment can be carried out reliably without being affected by other equipment.

[0090] refer to Figure 1 In some embodiments, the central rotary joint has an oil return port and an oil drain port 83, the oil return port being used to connect the oil return path of the upper multi-way valve group 3 to the radiator 14.

[0091] In some embodiments, the flow rate of the hydraulic check valve 71 is greater than that of the directional valve 72. In this embodiment, the hydraulic check valve 71 uses a high-flow-rate valve core, while the directional valve 72 uses a low-flow-rate valve core, which can greatly reduce the pressure drop during onboard operation, thereby reducing the impact on the onboard operation speed.

[0092] In another aspect of this disclosure, a construction machinery is provided, including a construction machinery control system, a loading mechanism, and a working mechanism as described in any of the above embodiments. The loading mechanism is configured to be connected to a loading multi-way valve group 3, and the working mechanism is configured to be connected to a hydraulic output port 4. The construction machinery includes, but is not limited to, emergency rescue vehicles, such as excavators, cranes, and aerial work platforms.

[0093] In this embodiment, the engineering machinery uses the engineering machinery control system to switch the oil supply and load feedback paths of the pump body 12 and the load-sensitive valve group 2 to achieve full pressure and full power output of the pump body 12. This makes the on-vehicle operation and the operation of external equipment relatively independent and do not affect each other. It can achieve a highly efficient and reliable operating state in each operating state, which helps to provide greater hydraulic output power for emergency rescue tools and improve the efficiency and safety of emergency rescue.

[0094] In some embodiments, the upper machinery includes a digging arm. In this embodiment, the working machinery can be an excavator. The upper multi-way valve group 3 includes an oil inlet link 31, a boom link 32, a stick link 33, a bucket link 34, a swing motor link 35, and a tail link 36. The oil inlet link 31 includes an unloading valve and a relief valve. The boom link 32 is connected to the large and small chambers of the boom cylinder 91. The stick link 33 is connected to the large and small chambers of the stick cylinder 92. The bucket link 34 is connected to the large and small chambers of the bucket cylinder 93. The swing motor link 35 is connected to the swing motor 94. The tail link 36 is connected to the swing motor 94 through a switching valve. The tail link 36 is used to release the brake on the swing motor 94.

[0095] The upper multi-way valve group 3 can be expanded according to actual needs, such as adding quick-change cylinder connection, tool oil supply connection, outrigger cylinder connection, pusher cylinder connection, travel motor connection, low-pressure hydraulic output connection, etc.

[0096] The pump body 12 and hydraulic oil tank 11 are located at the lower part of the vehicle, while the upper part of the vehicle has a multi-way valve group 3 and a cylinder. The pump body 12 and the actuator are connected through a central rotary joint. The remote control handle is connected to the processor 6 to control the energization sequence of the solenoid valves, thereby achieving digging and independent hydraulic output functions. This has little impact on the digging speed, and the hydraulic output pressure and power are high when using independent hydraulic output.

[0097] When the boom cylinder 91, stick cylinder 92, bucket cylinder 93, and slewing motor 94 need to operate individually or in combination, the power source 13 starts after high-voltage power is applied, driving the pump body 12 to a low-voltage standby state. The remote control handle sends an electrical signal to the corresponding multi-way valve in the upper multi-way valve group 3, driving the corresponding cylinder to extend or retract, or the motor to rotate, completing the digging and slewing actions.

[0098] During the excavation operation, the remote control toggle switch is switched to the upper structure working end. The controller 6 controls the first switch valve 51 and the second switch valve 52 to be de-energized. That is, the first switch valve 51 opens the oil circuit between the load feedback port 81 of the central rotary joint and the load sensitive valve group 2, and the second switch valve 52 closes the oil circuit between the hydraulic output port 4 and the load sensitive valve group 2. The load pressure fed back from the upper multi-way valve group 3 is fed back to the load sensitive valve group 2 of the pump body 12 through the load feedback port 81 of the central rotary joint and the first switch valve 51, so as to adjust the output pressure and flow of the pump body 12 in real time.

[0099] Simultaneously, the reversing valve 72 is in its first working position. The reversing valve 72 must not be electrically in the left position. Oil is discharged through the hydraulic control port of the hydraulic control check valve 71 via the left position of the reversing valve 72. The pressure oil output from the pump body 12 overcomes the spring force of the hydraulic control check valve 71, causing the hydraulic control check valve 71 to open. The pressure oil output from the pump body 12 flows into the upper multi-way valve group 3 after passing through the hydraulic control check valve 71 and the oil inlet port 82. The second switching valve group 7 has a small pressure drop during excavation flow, thus having little impact on the excavation speed of the upper structure.

[0100] When hydraulic output is required, the engine or motor must first be stopped. The oil inlet pipe of the external equipment is connected to the high-pressure hydraulic output port 41 in the hydraulic output port 4, and the oil return pipe of the external equipment is connected to the hydraulic output return port 42 in the hydraulic output port 4. After the high pressure is energized by the remote control, the motor or engine starts, driving the pump body 12 to a low-pressure standby state, and the pump body 12 outputs at a large displacement. When the remote control toggle switch is turned to the hydraulic output end, the controller 6 controls the first switch valve 51 and the second switch valve 52 to be energized. That is, the first switch valve 51 cuts off the oil circuit between the load feedback oil port 81 of the central rotary joint and the load sensitive valve group 2 to prevent the feedback oil circuit from overflowing through the upper multi-way valve group 3. The second switch valve 52 opens the oil circuit between the hydraulic output port 4 and the load sensitive valve group 2, and the load sensitive valve group 2 works under the action of spring force.

[0101] Simultaneously, the directional valve 72 is placed in the second working position, energized and in the right-hand position. The pressure oil from the pump body 12 is connected to the hydraulic control oil circuit of the hydraulic control check valve 71, thereby locking the hydraulic control check valve 71. The hydraulic oil output from the pump body 12 is cut off by the hydraulic control check valve 71, and the hydraulic oil output from the pump body 12 drives the external hydraulic equipment through the hydraulic output port 4. By adjusting the load of the external equipment, the maximum output power point of the pump body 12 can be obtained, outputting maximum power and pressure higher than the maximum output pressure of the multi-way valve group 3 on the excavation vehicle during excavation operations.

[0102] The embodiments of this disclosure have now been described in detail. To avoid obscuring the concept of this disclosure, some details known in the art have not been described. Those skilled in the art can fully understand how to implement the technical solutions disclosed herein based on the above description.

[0103] While specific embodiments of this disclosure have been described in detail by way of examples, those skilled in the art should understand that the examples are for illustrative purposes only and not intended to limit the scope of this disclosure. Those skilled in the art should understand that modifications can be made to the above embodiments or equivalent substitutions can be made to some technical features without departing from the scope and spirit of this disclosure. The scope of this disclosure is defined by the appended claims.

Claims

1. A control system for engineering machinery, used in engineering machinery, characterized in that, include: Fuel tank (11); The pump body (12) is connected to the oil tank (11); The power source (13) is poweredly connected to the pump body (12); A load-sensitive valve assembly (2) is connected to the pump body (12) to regulate the pressure and / or flow rate output by the pump body (12); The upper multi-way valve group (3) is connected to the pump body (12) and the load-sensitive valve group (2); The hydraulic output port (4) is connected to the pump body (12) and the oil tank (11) for connection with the working machinery; The first switching valve group (5), located in the oil passage between the load-sensitive valve group (2) and the upper vehicle multi-way valve group (3) and the oil passage between the load-sensitive valve group (2) and the hydraulic output port (4), is configured to selectively connect the oil passage between the load-sensitive valve group (2) and the upper vehicle multi-way valve group (3) or the oil passage between the load-sensitive valve group (2) and the hydraulic output port (4); The second switching valve group (7) is located in the oil passage between the pump body (12) and the upper vehicle multi-way valve group (3), and is configured to open or close the oil inlet between the pump body (12) and the upper vehicle multi-way valve group (3). A central rotary joint, located in the oil passage between the pump body (12) and the upper multi-way valve group (3), has a load feedback oil port (81); and The processor (6) is signal-connected to the first switching valve group (5); The first switching valve group (5) includes a first switching valve (51) and a second switching valve (52). The first switching valve (51) is located in the oil circuit between the load feedback oil port (81) of the central rotary joint and the load sensitive valve group (2). The second switching valve (52) is located in the oil circuit between the hydraulic output port (4) and the load sensitive valve group (2). The construction machinery has an on-board operation state and a hydraulic output state. The processor (6) is configured to enable the first switching valve group (5) to connect the oil circuit between the load-sensitive valve group (2) and the on-board multi-way valve group (3) in the on-board operation state, and to enable the first switching valve group (5) to connect the oil circuit between the load-sensitive valve group (2) and the hydraulic output port (4) in the hydraulic output state.

2. The engineering machinery control system as described in claim 1, characterized in that, The processor (6) is signal-connected to the second switching valve group (7) and is configured to enable the second switching valve group (7) to open the oil passage between the pump body (12) and the upper vehicle multi-way valve group (3) in the upper vehicle operation state, and to enable the second switching valve group (7) to close the oil passage between the pump body (12) and the upper vehicle multi-way valve group (3) in the hydraulic output state.

3. The engineering machinery control system as described in claim 2, characterized in that, The hydraulic output port (4) includes a quick-change interface or hydraulic plug, which is configured to cut off the pressure oil from the pump body (12) in the on-vehicle operation state.

4. The engineering machinery control system as described in claim 1, characterized in that, The first switching valve (51) has two working positions. When the first switching valve (51) is in the first working position, it opens the oil passage between the load feedback port (81) of the central rotary joint and the load sensitive valve group (2). When it is in the second working position, it closes the oil passage between the load feedback port (81) of the central rotary joint and the load sensitive valve group (2). The second switching valve (52) has two working positions. When the second switching valve (52) is in the first working position, it cuts off the oil passage between the hydraulic output port (4) and the load-sensitive valve group (2). When it is in the second working position, it opens the oil passage between the hydraulic output port (4) and the load-sensitive valve group (2). The processor (6) is signal-connected to the first switching valve (51) and the second switching valve (52). The processor (6) is configured to place the first switching valve (51) and the second switching valve (52) in a first working position in the on-vehicle operation state, and to place the first switching valve (51) and the second switching valve (52) in a second working position in the hydraulic output state.

5. The engineering machinery control system as described in claim 1, characterized in that, The central rotary joint has an oil inlet (82). The second switching valve group (7) includes: A hydraulically controlled check valve (71) is connected to the pump body (12) and the oil inlet (82) of the central rotary joint; and A reversing valve (72) is connected to the hydraulic control check valve (71), and the reversing valve (72) is configured to switch the pressure input state of the hydraulic control check valve (71) so that the hydraulic control check valve (71) adjusts the direction of the oil passage that is allowed to pass.

6. The engineering machinery control system as described in claim 5, characterized in that, The reversing valve (72) has two working positions. When the reversing valve (72) is in the first working position, it connects the oil passage between the hydraulic control check valve (71) and the oil tank (11) so that the hydraulic control check valve (71) can be opened from the pump body (12) to the upper vehicle multi-way valve group (3). When the reversing valve (72) is in the second working position, it connects the oil passage between the hydraulic control check valve (71) and the pump body (12) so that the hydraulic control check valve (71) can be opened from the pump body (12) to the upper vehicle multi-way valve group (3). The processor (6) is configured to place the reversing valve (72) in a first working position in the onboard operation state and in a second working position in the hydraulic output state.

7. The engineering machinery control system as described in claim 5, characterized in that, The valve core flow rate of the hydraulic control check valve (71) is greater than that of the directional valve (72).

8. An engineering machinery, characterized in that, include: The engineering machinery control system as described in any one of claims 1 to 7 above; The loading mechanism is configured to be connected to the loading multi-way valve group (3); The working machinery is configured to connect to the hydraulic output port (4).

9. The engineering machinery as described in claim 8, characterized in that, The loading machinery includes an excavator arm.

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