Intelligent multi-power drive control system

Abstract

The invention relates to the technical field of oil supplementation of hydraulic systems, in particular to an intelligent multi-power drive control system, when an intelligent steering system is reversed, a swash plate of a two-way variable pump completes power oil switching in a short time, a swash plate oil cylinder of the two-way variable pump swings to a negative maximum position from a positive maximum position, and the swash plate oil cylinder of the two-way variable pump is driven by the two-way variable pump. And pressure oil conversion output of the port A and the port B is completed. However, a main oil cylinder (a steering oil cylinder) still moves according to the previous trend due to dragging of wheel edge inertia, ultrahigh pressure occurs in a high-pressure cavity, ultralow pressure occurs in a low-pressure cavity, and meanwhile, the situation of air suction exists, one cavity of the main oil cylinder subjected to air suction can be supplemented with oil from a servo oil cylinder through a one-way valve, and the other cavity of the main oil cylinder subjected to air suction can be supplemented with oil through a one-way valve. The servo oil cylinder moves towards the oil-absorbed cavity to force the opening degree of the swash plate to be reduced, so that the impact of a hydraulic system is actively reduced; after a third one-way valve or a fourth one-way valve in the two-way variable pump is opened, the energy accumulator can also supplement oil to the system, and the continuity of pumping output is guaranteed.

Description

Technical Field

[0001] The present invention relates to the technical field of hydraulic system drive control, and in particular to an intelligent multi-power drive control system. Background Art

[0002] When the steering cylinder is changing direction, the swash plate of the main pump (bidirectional variable pump) swings from the maximum positive position to the maximum negative position within a very short period of time, and the pressure oil at ports A and B on the main pump will be converted.

[0003] However, due to the drag of the wheel side inertia, the main cylinder (steering cylinder) still moves according to its previous trend after the pressure oil at port A and port B is exchanged. Figure 1 , if the B port of the main pump outputs high-pressure oil, the main cylinder contracts, and the rodless chamber oil in the main cylinder can provide the main pump with suction oil (that is, the rodless chamber oil of the main cylinder meets the needs of the rod chamber). At this time, the system needs are met, but at the moment when the pressure oil exchange is completed, the main cylinder will continue to contract, which makes the high-pressure chamber prone to ultra-high pressure; on the contrary, after the steering system is reversed, the A port of the main pump outputs pressure oil. At this time, the rod chamber oil provides oil for the large chamber, which is obviously unable to meet the needs, and the rod chamber is sucked empty, which leads to the low-pressure chamber being prone to ultra-low pressure. If the ultra-low pressure is sucked empty, it will cause the low-pressure chamber to make sounds and vibrate, which affects the normal use of the subsequent system and reduces the service life of the system. Therefore, improvements are needed. Summary of the invention

[0004] In view of this, the purpose of the present invention is to propose an intelligent multi-power drive control system to solve the problem that when the turning cylinder suddenly reverses, the high-pressure chamber is prone to ultra-high pressure, the low-pressure chamber is prone to ultra-low pressure, and the ultra-low-pressure chamber is likely to be sucked empty, which will cause sound and vibration in the low-pressure chamber.

[0005] Based on the above purpose, the present invention provides an intelligent multi-power drive control system, including a two-way variable pump and a steering system, the steering system includes a steering cylinder, the two-way variable pump has an A port and a B port, and the A port of the two-way variable pump is connected to the rodless cavity of the steering cylinder through a pipeline A, and the B port of the two-way variable pump is connected to the rod cavity of the steering cylinder through a pipeline B, characterized in that it also includes a lifting system and a pump control system; the lifting system includes a lifting cylinder and a three-position four-way reversing valve, and the three-position four-way reversing valve has an A port, a B port, a P port and a T port, and the A port and the B port of the three-position four-way reversing valve are connected to the rod cavity of the steering cylinder. The ports are respectively connected to the rodless chamber and the rod chamber of the lifting cylinder, and the T port of the three-position four-way reversing valve 1 is connected to the hydraulic oil tank; the pump control system includes a metering pump, a relief valve group 1, a relief valve group 2, a three-position four-way reversing valve 2, a servo valve, a control rod and a servo cylinder; the P port of the three-position four-way reversing valve 1 is connected to the oil outlet of the metering pump, the relief valve group 1 includes an overload relief valve 1 and a check valve 1 arranged in parallel with each other, and the oil inlet of the overload relief valve 1 intersects with the oil outlet of the check valve 1 at P1, and P1 is connected to the pipeline B, and the oil outlet of the overload relief valve 1 intersects with the oil inlet of the check valve 1 at P2, and P2 is connected to the oil outlet of the metering pump through pipeline C, and pipeline C is connected to pipeline D, pipeline D is connected to the hydraulic oil tank, the overflow valve group 2 includes an overload overflow valve 2 and a check valve 2 arranged in parallel, and the oil outlet of the overload overflow valve 2 and the oil inlet of the check valve 2 intersect at P3, and P2 is connected to P3, the oil inlet of the overload overflow valve 2 and the oil outlet of the check valve 2 intersect at P4, and P4 is connected to pipeline A; when the B port of the two-way variable pump outputs high-pressure oil, the steering cylinder contracts, and the oil in the rodless chamber of the steering cylinder can meet the oil required by the rod chamber, After the cylinder is reversed, the A port of the two-way variable pump outputs pressure oil. At this time, the oil in the rod chamber of the steering cylinder cannot meet the oil required by the rodless chamber. At this time, the pressure oil output by the quantitative pump enters the low-pressure chamber pipeline B through the one-way valve 1 to supplement the high-pressure oil output of the A port at this time; and when the B port of the two-way variable pump outputs high-pressure oil, if it exceeds the set pressure of the load relief valve 1, the oil can be unloaded back to the hydraulic oil tank through the overload relief valve 1. When the A port of the two-way variable pump outputs high-pressure oil, if it exceeds the set pressure of the load relief valve 2, the oil can be unloaded back to the hydraulic oil tank through this valve;The three-position four-way reversing valve 2 has a P port, a T port and a B port, and the servo valve has a P port, a T port, an A port, a B port, and a control oil port C and a control oil port D distributed on both sides. The B port of the three-position four-way reversing valve 2 and the A port of the servo valve are both connected to the oil outlet of the metering pump, the P port and the T port of the three-position four-way reversing valve 2 are respectively connected to the control oil port C and the control oil port D of the servo valve, and the P port of the servo valve is connected to the left chamber of the servo oil cylinder, and the T port of the servo valve is connected to the right chamber of the servo oil cylinder. The valve core of the servo valve is connected to the piston rod on the right side of the servo oil cylinder through a control rod, so that the piston rod on the right side of the servo oil cylinder and the valve core of the servo valve move synchronously and in the same direction, and the piston rod on the left side of the servo oil cylinder is connected to the swash plate on the bidirectional variable pump, so that the movement of the piston rod on the left side or the piston rod on the right side of the servo oil cylinder can drive the swash plate of the bidirectional variable pump to swing, so as to adjust the displacement and displacement direction of the bidirectional variable pump. ;

[0006] Preferably, it also includes an oil replenishing system, which includes a one-way valve three and a one-way valve four, the oil inlet of the one-way valve three is connected to the left chamber of the servo cylinder, and the oil outlet of the one-way valve three is connected to the pipeline A, the oil inlet of the one-way valve four is connected to the right chamber of the servo cylinder, and the oil outlet of the one-way valve four is connected to the pipeline B.

[0007] When the steering system is changing direction, the swash plate on the two-way variable pump swings from the maximum positive position to the maximum negative position in a short time, that is, when the pressure oil at ports A and B is converted, the rod chamber on the steering cylinder that has been sucked empty can be replenished with oil from the servo cylinder through the four-way pipeline B of the one-way valve. The servo cylinder moves to the right position, that is, the piston rod on the right side of the servo cylinder moves toward the right chamber where oil is sucked, and the piston rod on the left side of the servo cylinder drives the swash plate of the two-way variable pump to rotate clockwise, so that the opening of the swash plate of the two-way variable pump becomes smaller, so as to reduce the impact on the system.

[0008] Preferably, the pump control system also includes a proportional pressure control valve, the oil inlet of the proportional pressure control valve is connected to the oil outlet of the metering pump, and the oil outlet of the proportional pressure control valve is connected to the B port of the three-position four-way reversing valve 2; when the three-position four-way reversing valve 2 is in the left position, the oil output by the metering pump passes through the proportional pressure control valve and the three-position four-way reversing valve 2 to reach the control oil port D of the servo valve, so that the proportional pressure control valve can control the real-time pressure of the oil, and the pressure oil that has not passed through the proportional pressure control valve can directly enter the servo valve and participate in the drive of the servo cylinder to achieve control agility.

[0009] Preferably, the pump control system also includes an overload relief valve three, the oil inlet of the overload relief valve three is connected to the oil outlet of the metering pump, and the oil outlet of the overload relief valve three is connected to the hydraulic oil tank. When the lifting cylinder is overloaded and exceeds the protection pressure set by the overload relief valve three, the hydraulic oil can be unloaded through the overload relief valve three and flow back to the hydraulic oil tank, thereby protecting the metering pump.

[0010] Preferably, a stop valve is connected to the oil outlet of pipeline D, and the pump control system also includes an accumulator, a pressure detection point, a back pressure check valve and an electronically controlled overflow valve, and the accumulator is connected to pipeline D through pipeline E, and the pressure detection point, the back pressure check valve and the electronically controlled overflow valve are arranged in parallel on pipeline E. The adjustable pressure control of the electronically controlled overflow valve can control the pressure of the pressure oil output by the accumulator in real time according to the system pressure requirement, and the pressure detection point can monitor the internal state of the accumulator in real time to determine whether the accumulator is discharging liquid or absorbing the pressure shock in the system, and when the system shock reaches the pressure set by the back pressure check valve, the accumulator can be filled with liquid, so that the accumulator is continuously charged and discharged in the system to meet the system requirements.

[0011] Preferably, the oil inlet of the metering pump is connected to the hydraulic oil tank, and an oil suction filter is connected to the oil inlet of the metering pump. The oil suction filter is connected in parallel with a constant pressure one-way valve, and a buzzer is connected to the constant pressure one-way valve. During the oil suction process, if the oil suction filter is blocked, the hydraulic oil can enter the system through the constant pressure one-way valve. The spring force of the constant pressure one-way valve can be adjusted according to demand. When the spring is pushed open, the buzzer alarm sounds and sends out an over-pressure protection electrical signal to prompt the replacement of the oil suction filter element in the oil suction filter.

[0012] Preferably, the pump control system further comprises a power source and a clutch, and the transmission shafts of the fixed displacement pump and the bidirectional variable displacement pump are connected to the rotating shaft in the power source via the clutch.

[0013] Preferably, the steering cylinder and the lifting cylinder are both fixedly connected with guide rods via guide rod brackets, and movement sensors are installed on the steering cylinder and the lifting cylinder. The movement sensors can move along the guide rods with the cylinder piston rods, and end point limiters are also installed at the ends of the guide rod brackets.

[0014] The beneficial effects of the present invention are as follows: To ensure the safety of operation and vehicle running, the steering system and lifting system cannot operate at the same time.

[0015] Overload relief valve three can ensure that when the lifting cylinder is overloaded, the hydraulic oil can be unloaded and flow back to the oil tank, thereby protecting the metering pump; when the two-way variable pump outputs high-pressure oil from port A, that is, the oil pressure in pipeline A exceeds the set pressure of overload relief valve two, the high-pressure oil in pipeline A can flow back to the hydraulic oil tank through overload relief valve two, and when port B outputs high-pressure oil, that is, the oil pressure in pipeline B exceeds the set pressure of overload relief valve one, the high-pressure oil in pipeline B can flow back to the hydraulic oil tank through overload relief valve one. In summary, overload relief valve one, overload relief valve two and overload relief valve three ensure that the hydraulic oil can be unloaded in the case of overload, thereby protecting system components.

[0016] When the steering system is changing direction, the swash plate of the two-way variable pump swings from the maximum positive position to the maximum negative position in a short time, and the pressure oil pressure of ports A and B is converted. After the steering cylinder changes direction, the pressure oil is output from port A of the two-way variable pump. At this time, the oil in the rod chamber of the steering cylinder cannot meet the oil required by the rodless chamber. At this time, the pressure oil output by the metering pump enters the low-pressure chamber pipeline B through the one-way valve 1 to supplement the oil output of the high-pressure oil at port A. At the same time, the rod chamber sucked empty on the steering cylinder can be replenished from the servo cylinder through the one-way valve 4 to the pipeline B. The servo cylinder moves to the right position, that is, the piston rod on the right side of the servo cylinder moves toward the right chamber where the oil is sucked. The piston rod on the left side of the servo cylinder will drive the swash plate of the two-way variable pump to rotate clockwise, so that the opening of the swash plate of the two-way variable pump becomes smaller, so as to reduce the impact on the system; and after the oil replenishment check valve 3 or the oil replenishment check valve 4 inside the main pump is opened, the accumulator replenishes oil to the system to ensure the continuity of pumping.

[0017] 4. When the second three-position four-way directional valve moves to the left position, the servo valve moves in the middle position, and the oil output by the metering pump passes through the proportional pressure control valve and the second three-position four-way directional valve to reach the control oil port D of the servo valve. When the second three-position four-way directional valve moves to the right position, the servo valve moves in the middle position, and the oil drawn by the metering pump enters the servo valve through the control oil port C, so that the proportional pressure control valve can control the real-time pressure of the oil, and the pressure oil that has not passed through the proportional pressure control valve can directly enter the servo valve and participate in the drive of the servo cylinder to achieve control agility. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are only embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0019] Figure 1It is a schematic diagram of the main pump supplying oil to the steering cylinder in the background technology of the present invention; Figure 2 It is a structural schematic diagram of an embodiment of the present invention; Figure 3 Schematic diagram of the structure of the steering cylinder and the movement sensor in the embodiment of the present invention.

[0020] In the figure: 11, oil suction filter; 11-1, constant pressure one-way valve; 11-2, buzzer; 12, accumulator; 13, one-way valve three; 14, one-way valve four; 15, overload relief valve two; 16, fixed displacement pump; 17, overload relief valve three; 18, overload relief valve one; 19, control rod; 20, servo cylinder; 21, two-way variable pump; 22, power source; 23, servo valve; 24, steering cylinder; 26, three-position four-way reversing valve one; 27, lifting cylinder; 28, proportional pressure control valve; 29, three-position four-way reversing valve two; 33, guide rod bracket; 35, moving sensor; 36, guide rod; 37, end limiter; 100, electric control relief valve; 101, stop valve; 102, back pressure one-way valve; 103, pressure detection point. DETAILED DESCRIPTION

[0021] In order to make the objectives, technical solutions and advantages of the present invention more clearly understood, the present invention is further described in detail below in conjunction with specific embodiments and with reference to the accompanying drawings.

[0022] It should be noted that, unless otherwise defined, the technical terms or scientific terms used in the embodiments of the present invention should be understood by people with ordinary skills in the field to which the present invention belongs. The "first", "second" and similar words used in the present invention do not represent any order, quantity or importance, but are only used to distinguish different components. "Including" or "comprising" and similar words mean that the elements or objects appearing before the word cover the elements or objects listed after the word and their equivalents, without excluding other elements or objects. "Connecting" or "connected" and similar words are not limited to physical or mechanical connections, but can include electrical connections, whether direct or indirect. "Up", "down", "left", "right" and the like are only used to indicate relative positional relationships. When the absolute position of the described object changes, the relative positional relationship may also change accordingly.

[0023] like Figure 1 , Figure 2 , Figure 3As shown, an intelligent multi-power drive control system includes a bidirectional variable pump 21 and a steering system, the steering system includes a steering cylinder 24, the bidirectional variable pump 21 has an A port and a B port, and the A port of the bidirectional variable pump 21 is connected to the rodless cavity of the steering cylinder 24 through a pipeline A, and the B port of the bidirectional variable pump 21 is connected to the rod cavity of the steering cylinder 24 through a pipeline B, characterized in that it also includes a lifting system and a pump control system; The lifting system includes a lifting cylinder 27 and a three-position four-way reversing valve 26, and the three-position four-way reversing valve 26 has an A port, a B port, a P port and a T port, and the A port and the B port of the three-position four-way reversing valve 26 are respectively connected to the rodless cavity and the rod cavity of the lifting cylinder 27, and the T port of the three-position four-way reversing valve 26 is connected to the hydraulic oil tank; The pump control system includes a metering pump 16, a relief valve group 1, a relief valve group 2, a three-position four-way reversing valve 29, a servo valve 23, a control rod 19 and a servo cylinder 20; The pump control system further includes a power source 22 and a clutch. The transmission shafts of the metering pump 16 and the bidirectional variable pump 21 are connected to the rotating shaft in the power source 22 via the clutch.

[0024] The P port of the three-position four-way reversing valve 26 is connected to the oil outlet of the metering pump 16. The overflow valve group 1 includes an overload overflow valve 18 and a check valve 1 which are arranged in parallel with each other. The oil inlet of the overload overflow valve 18 intersects with the oil outlet of the check valve 1 at P1, and P1 is connected to the pipeline B. The oil outlet of the overload overflow valve 18 intersects with the oil inlet of the check valve 1 at P2, and P2 is connected to the metering pump 16 through the pipeline C. The oil outlet of the overload relief valve 15 is connected to the oil outlet of the overload relief valve 15, and the oil outlet of the overload relief valve 15 intersects with the oil inlet of the one-way valve 15 at P3, and P2 is connected to P3, the oil inlet of the overload relief valve 15 intersects with the oil outlet of the one-way valve 15 at P4, and P4 is connected to the pipeline A. ; When the B port of the two-way variable pump 21 outputs high-pressure oil, the steering cylinder 24 contracts, and the oil in the rodless chamber of the steering cylinder 24 can meet the oil required by the rod chamber. After the steering cylinder 24 changes direction, the A port of the two-way variable pump 21 outputs pressure oil. At this time, the oil in the rod chamber of the steering cylinder 24 cannot meet the oil required by the rodless chamber. At this time, the pressure oil output by the metering pump 16 enters the low-pressure chamber pipeline B through the one-way valve 1 at this time, and supplements the oil volume of the high-pressure oil output at the A port at this time; the one-way valve 1 set in parallel with the overload relief valve 18 can be turned on when the B port needs to be supplemented with oil. When the B port outputs high pressure, the overload relief valve 18 plays a role in protecting the system. The one-way valve 2 set in parallel with the overload relief valve 2 15 can be turned on when the A port needs to be supplemented with oil, and high-pressure oil is output at the A port. The overload relief valve 2 15 plays a role in protecting the system.

[0025] When the high-pressure oil is output from the port B of the two-way variable pump 21, if the pressure exceeds the set pressure of the overload relief valve 18, the oil can be unloaded back to the hydraulic oil tank through the overload relief valve 18. When the high-pressure oil is output from the port A of the two-way variable pump 21, if the pressure exceeds the set pressure of the overload relief valve 15, the oil can be unloaded back to the hydraulic oil tank through this valve. The three-position four-way reversing valve 29 has a P port, a T port and a B port, and the servo valve 23 has a P port, a T port, an A port, a B port, and a control oil port C and a control oil port D distributed on both sides. The B port of the three-position four-way reversing valve 29 and the A port of the servo valve 23 are both connected to the oil outlet of the metering pump 16, and the P port and the T port of the three-position four-way reversing valve 29 are respectively connected to the control oil port C and the control oil port D of the servo valve 23, and the P port of the servo valve 23 is connected to the left chamber of the servo cylinder 20, and the T port of the servo valve 23 is connected to the left chamber of the servo cylinder 20. The right chamber of the servo cylinder 20 is connected, and the valve core of the servo valve 23 is connected to the piston rod on the right side of the servo cylinder 20 through the control rod 19, so that the piston rod on the right side of the servo cylinder 20 and the valve core of the servo valve 23 move synchronously and in the same direction, and the piston rod on the left side of the servo cylinder 20 is connected to the swash plate on the two-way variable pump 21, so that the movement of the piston rod on the left side or the right side of the servo cylinder 20 can drive the swash plate of the two-way variable pump 21 to swing, so as to adjust the displacement and displacement direction of the two-way variable pump 21.

[0026] In a preferred embodiment of the present invention, it also includes an oil replenishing system, which includes a one-way valve three 13 and a one-way valve four 14. The oil inlet of the one-way valve three 13 is connected to the left chamber of the servo cylinder 20, and the oil outlet of the one-way valve three 13 is connected to the pipeline A, the oil inlet of the one-way valve four 14 is connected to the right chamber of the servo cylinder 20, and the oil outlet of the one-way valve four 14 is connected to the pipeline B.

[0027] When the steering system is changing direction, the swash plate on the two-way variable pump 21 swings from the maximum positive position to the maximum negative position in a short time, that is, when the pressure oil at ports A and B is converted, the rod chamber on the steering cylinder 24 that has been sucked empty can be replenished with oil from the servo cylinder 20 to the pipeline B through the one-way valve 414, and the servo cylinder 20 moves to the right position, that is, the piston rod on the right side of the servo cylinder 20 moves toward the right chamber where oil is sucked, and the piston rod on the left side of the servo cylinder 20 will drive the swash plate of the two-way variable pump 21 to rotate clockwise, so that the opening of the swash plate of the two-way variable pump 21 becomes smaller, so as to reduce the impact on the system.

[0028] In a preferred embodiment of the present invention, the pump control system also includes a proportional pressure control valve 28, the oil inlet of the proportional pressure control valve 28 is connected to the oil outlet of the metering pump 16, and the oil outlet of the proportional pressure control valve 28 is connected to the B port of the three-position four-way reversing valve 29; when the three-position four-way reversing valve 29 is in the left position, the oil output by the metering pump 16 passes through the proportional pressure control valve 28 and the three-position four-way reversing valve 29 to reach the control oil port D of the servo valve 23, so that the proportional pressure control valve 28 can control the real-time pressure of the oil, and the pressure oil that has not passed through the proportional pressure control valve 28 can directly enter the servo valve 23 and participate in the drive of the servo cylinder 20 to achieve control agility.

[0029] The metering pump 16 is in motion, the three-position four-way reversing valve 1 26 is not in motion, and the pressure oil of the metering pump 16 enters the proportional control pressure valve 28. When the three-position four-way reversing valve 2 29 is not powered, the servo cylinder 20 does not work, the three-position four-way reversing valve 2 29 is in the middle position, and the swash plate of the two-way variable pump 21 is also in the middle position, and there is no pressure output at this time; when the three-position four-way reversing valve 2 29 is in the left position, that is, when the left end of the three-position four-way reversing valve 2 29 is powered, the servo valve 23 is in the middle position, and the oil of the metering pump 16 enters the servo valve 23 through the control oil port D, and the piston of the servo valve 23 moves to the left, and the servo valve 23 is brought to the control rod 19 together to ensure the stability of the servo valve 23. The piston rod on the left side of the servo cylinder 20 pushes the swash plate of the two-way variable pump 21 to rotate counterclockwise. At this time, the B port of the two-way variable pump 21 outputs high-pressure oil, and the steering cylinder 24 contracts.

[0030] When the three-position four-way reversing valve 29 is in the right position, the servo valve 23 is in the middle position, and the oil drawn by the metering pump 16 enters the servo valve 23 through the control oil port C. The piston of the servo valve 23 moves to the right, and also drives the control rod 19 to move. The piston rod on the right side of the servo cylinder 20 pushes the swash plate of the two-way variable pump 21 to rotate clockwise. At this time, the A port of the two-way variable pump 21 sprays high-pressure oil, and the rodless chamber of the steering cylinder 24 enters oil, and the steering cylinder 24 extends.

[0031] When the three-position four-way reversing valve 29 is in the middle position, the oil pumped by the metering pump 16 will directly enter the servo valve 23. The specific process is as follows: when the servo valve 23 is in the right position, the oil pumped by the metering pump 16 enters the right chamber of the servo cylinder 20 through the A port and T port of the servo valve 23, thereby pushing the piston rod of the servo cylinder 20 to move leftward. The left piston rod of the servo cylinder 20 can push the swash plate of the two-way variable pump 21 to rotate counterclockwise. At this time, the two-way variable pump The B port of 21 outputs high-pressure oil, and the steering cylinder 24 contracts; when the servo valve 23 is in the left position, the oil drawn by the metering pump 16 enters the left chamber of the servo cylinder 20 through the A port and P port of the servo, thereby pushing the piston rod of the servo cylinder 20 to move right, and the piston rod on the right side of the servo cylinder 20 pushes the swash plate of the two-way variable pump 21 to rotate clockwise. At this time, the A port of the two-way variable pump 21 sprays high-pressure oil, and the steering cylinder 24 has no rod chamber and oil enters, and the steering cylinder 24 extends.

[0032] In summary, the oil outlet of the metering pump 16 is not only the control oil provider of the pump control system, but also the driving oil of the bidirectional variable pump 21 and the servo cylinder 20. It is also the oil replenishment pump of the A and B ports of the bidirectional variable pump 21, and the power system of the lifting system.

[0033] In a preferred embodiment of the present invention, the pump control system also includes an overload relief valve 17, the oil inlet of the overload relief valve 17 is connected to the oil outlet of the metering pump 16, and the oil outlet of the overload relief valve 17 is connected to the hydraulic oil tank. When the lifting cylinder 27 is overloaded and exceeds the protection pressure set by the overload relief valve 17, the hydraulic oil can be unloaded through the overload relief valve 17 and flow back to the hydraulic oil tank, thereby protecting the metering pump 16.

[0034] In a preferred embodiment of the present invention, a stop valve 101 is connected to the oil outlet of pipeline D, and the pump control system also includes an accumulator 12, a pressure detection point 103, a back pressure check valve 102 and an electronically controlled overflow valve 100, and the accumulator 12 is connected to the pipeline D through a pipeline E, and the pressure detection point 103 and the back pressure check valve 102 are arranged in parallel with the electronically controlled overflow valve 100 on the pipeline E. The adjustable pressure control of the electronically controlled overflow valve 100 can control the pressure of the pressure oil output by the accumulator 12 in real time according to the system pressure requirement, and the pressure detection point 103 can monitor the internal state of the accumulator 12 in real time to determine whether the accumulator 12 is discharging liquid or absorbing the pressure shock in the system, and when the system shock reaches the pressure set by the back pressure check valve 102, the accumulator 12 can be filled with liquid, so that the accumulator 12 is continuously charged and discharged in the system to meet the system requirements.

[0035] After the stop valve 101 is opened, the entire system is unloaded, and safe maintenance can be carried out at this time. Before the steering system is operated, the metering pump 16 first fills the accumulator 12 with liquid through the pressed one-way valve 102. The initial state of the lifting system when working is that the metering pump 16 sucks hydraulic oil from the hydraulic oil tank to store energy and press the accumulator 12, so that the accumulator 12 reaches the preset pressure of the electronically controlled relief valve 100, that is, the accumulator 12 is in a working state at this time. When the steering is reversed or the lifting action is performed, the accumulator 12 can release energy to meet the system. When the system has an impact, the accumulator 12 can also absorb energy to stabilize the system. The pressure detection point 103 monitors the pressure of the accumulator 12 at all times, so that it can be intuitively judged that it can enter the working state.

[0036] In another preferred embodiment of the present invention, the oil inlet of the metering pump 16 is connected to the hydraulic oil tank, and the oil inlet of the metering pump 16 is connected to an oil suction filter 11, the oil suction filter 11 is connected in parallel with a constant pressure check valve 11-1, and the constant pressure check valve 11-1 is connected to a buzzer 11-2. During the oil suction process, if the oil suction filter 11 is blocked, the hydraulic oil can enter the system through the constant pressure check valve 11-1. The spring force of the constant pressure check valve 11-1 can be adjusted according to demand. When the spring is pushed open, the buzzer alarm 11-2 sounds and sends an over-pressure protection electrical signal to prompt the replacement of the oil suction filter element in the oil suction filter 11, so as to ensure the cleanliness of the system and prevent the system from being damaged due to oil contamination.

[0037] In another preferred embodiment of the present invention, the steering cylinder 24 and the lifting cylinder 27 are both fixedly connected with a guide rod 36 through a guide rod bracket 33, and a movement sensor 35 is installed on the steering cylinder 24 and the lifting cylinder 27. The movement sensor 35 can move along the guide rod 36 with the cylinder piston rod, and an end limiter 37 is also installed at the end of the guide rod bracket 33. The movement sensor 35 outputs a position signal in real time to form feedback with the hydraulic system, thereby further ensuring the accuracy of system control.

[0038] Those skilled in the art should understand that the discussion of any of the above embodiments is merely illustrative and is not intended to imply that the scope of the present invention is limited to these examples. Under the concept of the present invention, the technical features in the above embodiments or different embodiments may be combined, the steps may be implemented in any order, and there are many other variations of the different aspects of the present invention as described above, which are not provided in detail for the sake of simplicity.

[0039] The embodiments of the present invention are intended to cover all such substitutions, modifications and variations that fall within the broad scope of the appended claims. Therefore, any omissions, modifications, equivalent substitutions, improvements, etc. made within the spirit and principles of the present invention should be included in the protection scope of the present invention.

Claims

1. An intelligent multi-power drive control system, comprising a bidirectional variable pump (21) and a steering system, wherein the steering system comprises a steering cylinder (24), wherein the bidirectional variable pump (21) has an A port and a B port, and the A port of the bidirectional variable pump (21) is connected to a rodless cavity of the steering cylinder (24) through a pipeline A, and the B port of the bidirectional variable pump (21) is connected to a rod cavity of the steering cylinder (24) through a pipeline B, wherein: It also includes a lifting system and a pump control system; the lifting system includes a lifting cylinder (27) and a three-position four-way reversing valve (26), and the three-position four-way reversing valve (26) has an A port, a B port, a P port and a T port, and the A port and the B port of the three-position four-way reversing valve (26) are respectively connected to the rodless cavity and the rod cavity of the lifting cylinder (27), and the T port of the three-position four-way reversing valve (26) is connected to the hydraulic oil tank; the pump control system includes a metering pump (16), a relief valve group (1), a relief valve group (2), a three-position four-way reversing valve (29), a servo valve (23), a control rod (19) and a servo oil tank. cylinder (20); the P port of the three-position four-way reversing valve (26) is connected to the oil outlet of the metering pump (16); the relief valve group (1) includes an overload relief valve (18) and a check valve (1) which are arranged in parallel with each other, and the oil inlet of the overload relief valve (18) and the oil outlet of the check valve (1) intersect at P1, and P1 is connected to the pipeline B, the oil outlet of the overload relief valve (18) and the oil inlet of the check valve (1) intersect at P2, and P2 is connected to the oil outlet of the metering pump (16) through the pipeline C, and the pipeline C is connected to the pipeline D, and the pipeline D is connected to the hydraulic oil tank, and the relief valve group (2) includes an overload relief valve (18) and a check valve (1) which are arranged in parallel with each other. An overload relief valve 2 (15) and a check valve 2 are connected, and the oil outlet of the overload relief valve 2 (15) intersects with the oil inlet of the check valve 2 at P3, and P2 is connected to P3, the oil inlet of the overload relief valve 2 (15) intersects with the oil outlet of the check valve 2 at P4, and P4 is connected to the pipeline A; when the B port of the two-way variable pump (21) outputs high-pressure oil, the steering cylinder (24) contracts, and the oil in the rodless chamber of the steering cylinder (24) can meet the oil required by the rod chamber. After the steering cylinder (24) is reversed, that is, the A port of the two-way variable pump (21) outputs pressure oil, the steering cylinder (24) is When the oil in the rod chamber of (24) cannot meet the oil required by the rodless chamber, the pressure oil output by the metering pump (16) enters the low-pressure chamber pipeline B through the one-way valve 1 to supplement the high-pressure oil output at the A port; and when the high-pressure oil is output from the B port of the bidirectional variable pump (21), if the pressure exceeds the set pressure of the overload relief valve 1 (18), the oil can be unloaded back to the hydraulic oil tank through the overload relief valve 1 (18); when the high-pressure oil is output from the A port of the bidirectional variable pump (21), if the pressure exceeds the set pressure of the overload relief valve 2 (15), the oil can be unloaded back to the hydraulic oil tank through this valve;The three-position four-way reversing valve (29) has a P port, a T port and a B port. The servo valve (23) has a P port, a T port, an A port, a B port, and a control oil port C and a control oil port D distributed on both sides. The B port of the three-position four-way reversing valve (29) and the A port of the servo valve (23) are both connected to the oil outlet of the metering pump (16). The P port and the T port of the three-position four-way reversing valve (29) are respectively connected to the control oil port C and the control oil port D of the servo valve (23). The P port of the servo valve (23) is connected to the left chamber of the servo oil cylinder (20). The T port of the servo valve (23) is connected to the left chamber of the servo oil cylinder (20). The control rod (19) is connected to the right chamber of the servo oil cylinder (20), and the valve core of the servo valve (23) is connected to the piston rod on the right side of the servo oil cylinder (20), so that the piston rod on the right side of the servo oil cylinder (20) and the valve core of the servo valve (23) move synchronously and in the same direction. The piston rod on the left side of the servo oil cylinder (20) is connected to the swash plate on the bidirectional variable pump (21), so that the movement of the piston rod on the left side or the piston rod on the right side of the servo oil cylinder (20) can drive the swash plate of the bidirectional variable pump (21) to swing, so as to adjust the displacement and displacement direction of the bidirectional variable pump (21).

2. The intelligent multi-power drive control system according to claim 1, characterized in that: It also includes an oil replenishing system, which includes a one-way valve three (13) and a one-way valve four (14), the oil inlet of the one-way valve three (13) is connected to the left chamber of the servo cylinder (20), and the oil outlet of the one-way valve three (13) is connected to the pipeline A, the oil inlet of the one-way valve four (14) is connected to the right chamber of the servo cylinder (20), and the oil outlet of the one-way valve four (14) is connected to the pipeline B.

3. When the steering system is switching, the swash plate on the bidirectional variable pump (21) swings from the maximum positive position to the maximum negative position in a short time, that is, when the pressure oil at ports A and B is converted, the rod chamber on the steering cylinder (24) that has been sucked empty can be replenished with oil from the servo cylinder (20) through the one-way valve 4 (14) to the pipeline B, and the servo cylinder (20) moves to the right position, that is, the piston rod on the right side of the servo cylinder (20) moves toward the right chamber where the oil is sucked, and the piston rod on the left side of the servo cylinder (20) drives the swash plate of the bidirectional variable pump (21) to rotate clockwise, so that the opening of the swash plate of the bidirectional variable pump (21) becomes smaller, so as to reduce the impact on the system.

4. The intelligent multi-power drive control system according to claim 1, characterized in that: The pump control system further comprises a proportional pressure control valve (28), the oil inlet of the proportional pressure control valve (28) being connected to the oil outlet of the metering pump (16), and the oil outlet of the proportional pressure control valve (28) being connected to the B port of the second three-position four-way reversing valve (29); When the three-position four-way reversing valve (29) is in the left position, the oil output by the metering pump (16) passes through the proportional pressure control valve (28) and the three-position four-way reversing valve (29) to reach the control oil port D of the servo valve (23), so that the proportional pressure control valve (28) can control the real-time pressure of the oil, and the pressure oil that has not passed through the proportional pressure control valve (28) can directly enter the servo valve (23) to participate in the driving of the servo cylinder (20), so as to achieve control agility.

5. The intelligent multi-power drive control system according to claim 1, characterized in that: The pump control system further comprises an overload relief valve three (17), the oil inlet of the overload relief valve three (17) being connected to the oil outlet of the metering pump (16), and the oil outlet of the overload relief valve three (17) being connected to the hydraulic oil tank. When the lifting cylinder (27) is overloaded and exceeds the protection pressure set by the overload relief valve three (17), the hydraulic oil can be unloaded and flow back to the hydraulic oil tank through the overload relief valve three (17), thereby protecting the metering pump (16).

6. The intelligent multi-power drive control system according to claim 1, characterized in that: A stop valve (101) is connected to the oil outlet of the pipeline D. The pump control system further comprises an accumulator (12), a pressure detection point (103), a back pressure check valve (102) and an electronically controlled overflow valve (100). The accumulator (12) is connected to the pipeline D via a pipeline E. The pressure detection point (103), the back pressure check valve (102) and the electronically controlled overflow valve (100) are arranged in parallel on the pipeline E. The adjustable pressure control of the electronically controlled overflow valve (100) can control the pressure of the pressure oil output by the accumulator (12) in real time according to the system pressure demand. The pressure detection point (103) can monitor the internal state of the accumulator (12) in real time to judge whether the accumulator (12) is discharging liquid or absorbing the pressure shock in the system. When the system shock reaches the pressure set by the back pressure check valve (102), the accumulator (12) can be filled with liquid, so that the accumulator (12) is continuously charged and discharged in the system, thereby meeting the system demand.

7. The intelligent multi-power drive control system according to claim 1, characterized in that: The oil inlet of the metering pump (16) is connected to the hydraulic oil tank, and the oil inlet of the metering pump (16) is connected to an oil suction filter (11). The oil suction filter (11) is connected in parallel with a constant pressure check valve (11-1), and the constant pressure check valve (11-1) is connected to a buzzer (11-2). During the oil suction process, if the oil suction filter (11) is blocked, hydraulic oil can enter the system through the constant pressure check valve (11-1). The spring force of the constant pressure check valve (11-1) can be adjusted according to demand. When the spring is pushed open, the buzzer alarm (11-2) sounds and sends an overpressure protection electrical signal to prompt the replacement of the oil suction filter element in the oil suction filter (11).

8. The intelligent multi-power drive control system according to claim 1, characterized in that: The pump control system further comprises a power source (22) and a clutch, and the transmission shafts of the fixed displacement pump (16) and the bidirectional variable displacement pump (21) are connected to the rotating shaft in the power source (22) via the clutch.

9. The intelligent multi-power drive control system according to claim 1, characterized in that: The steering cylinder (24) and the lifting cylinder (27) are both fixedly connected to a guide rod (36) via a guide rod bracket (33), and a movement sensor (35) is installed on the steering cylinder (24) and the lifting cylinder (27). The movement sensor (35) can move along the guide rod (36) with the cylinder piston rod, and an end point limiter (37) is also installed at the end of the guide rod bracket (33).

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