CN114622618A - Novel load rotating speed double-sensitive system, engineering mechanical device and control method thereof - Google Patents
Novel load rotating speed double-sensitive system, engineering mechanical device and control method thereof Download PDFInfo
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- CN114622618A CN114622618A CN202210372145.9A CN202210372145A CN114622618A CN 114622618 A CN114622618 A CN 114622618A CN 202210372145 A CN202210372145 A CN 202210372145A CN 114622618 A CN114622618 A CN 114622618A
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- 239000010720 hydraulic oil Substances 0.000 claims description 14
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2264—Arrangements or adaptations of elements for hydraulic drives
- E02F9/2267—Valves or distributors
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2278—Hydraulic circuits
- E02F9/2292—Systems with two or more pumps
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Abstract
The invention provides a novel load rotating speed double-sensing system, an engineering mechanical device and a control method thereof, which realize the flow matching of a hydraulic pump by detecting the maximum load pressure, control the difference value between the outlet pressure of a main pump and the maximum load pressure to be a certain control value, control the control value by a rotating speed sensing valve bank based on the rotating speed of a power source, reduce the target control pressure difference between the outlet pressure of the hydraulic pump and the maximum load pressure under the condition of low-speed operation of the power source, further reduce the pressure difference of a throttling port of the rotating speed sensing valve bank, reduce the corresponding proportional relation of the oil supply flow of a system, a pilot signal and the target flow, and improve the control precision of the pilot signal on the target flow. Under the condition that a power source runs at a high speed, the target control pressure difference between the outlet pressure of the main pump and the maximum load pressure is increased, so that the pressure difference of a throttling port of the rotating speed sensitive valve group is increased, the corresponding proportional relation of the oil supply flow, the pilot signal and the target flow of the system and the through-flow capacity of the unit opening of the throttling valve port are improved, and the action speed of the system is further improved.
Description
Technical Field
The invention relates to the field of hydraulic systems, in particular to a novel load rotating speed double-sensitive system, an engineering mechanical device and a control method thereof.
Background
Engineering machinery is widely applied to various earthwork construction fields. However, the conventional construction machine has the disadvantages of limited flow rate and pressure matching characteristics, poor controllability and the like. The typical hydraulic system of the engineering machinery can be divided into a negative flow system, a positive flow system, a load sensitive system and the like mainly according to different flow matching modes. The load sensitive system is based on a closed center oil way, the maximum load pressure is detected and fed back to control the displacement of the hydraulic pump, so that the outlet pressure of the hydraulic pump is only higher than the maximum load pressure value by a fixed value, the pressure difference of each throttle valve port is maintained to be a preset value through the pressure compensation valve, the through flow of the throttle valve is only related to the opening area of the throttle valve and is not related to the load, and the controllability is improved. However, since the differential pressure value of the conventional load-sensitive system is a set value of a system spring, the differential pressure is constant during the working process, and although the adjustment characteristic of the throttle valve is not affected by load change compared with a negative flow and positive flow system, the differential pressure cannot adapt to requirements of different working conditions, such as fine operation and rapid operation, the same differential pressure cannot simultaneously meet requirements of process wide-stroke control of the fine operation and large-flow output during the rapid operation.
In view of this, the present application is presented.
Disclosure of Invention
The invention discloses a novel load rotating speed double-sensing system, an engineering mechanical device and a control method thereof, aiming at solving the problem that the same pressure difference cannot simultaneously give consideration to the wide-stroke control of a fine operation process and the large-flow output requirement of a rapid operation process.
The first embodiment of the present invention provides a novel load rotation speed dual sensing system, which includes: the system comprises a main pump source, a pilot pump, a rotating speed sensitive valve group, a load sensitive system, a first actuator and a second actuator;
the main pump source is connected with the first actuator and the second actuator through the load sensitive system, the main pump source is coaxially connected with the pilot pump, and the pilot pump is connected with the main pump source and the load sensitive system through the rotating speed sensitive valve bank;
the rotating speed sensitive valve group is configured to monitor the rotating speed of a main pump source and adjust the target control pressure difference of the load sensitive system according to the rotating speed of the main pump source.
Preferably, the main pump source includes: the system comprises a power source, a main pump, a first two-position three-way reversing valve, a first displacement adjusting mechanism and a second displacement adjusting mechanism;
the output shaft of power supply with the main pump machinery links to each other, the input of main pump is used for being connected with hydraulic tank, the control mouth of the first discharge capacity adjustment mechanism of output of main pump is connected, the B mouth of first two-position three-way switching-over valve with hydraulic tank connects, the P mouth of first two-position three-way switching-over valve the second discharge capacity adjustment mechanism is connected, the A mouth of first two-position three-way switching-over valve with the sensitive valves of rotational speed is connected, the upper and lower control chamber of first two-position three-way switching-over valve with the sensitive systemic connection of load.
Preferably, the speed sensitive valve set comprises: a first two-position two-way reversing valve and a second two-position three-way reversing valve;
the input end of the pilot pump is used for being connected with a hydraulic oil tank, the output end of the pilot pump is connected with a P port and a left side control cavity of the first two-position two-way reversing valve, a lower side control cavity of the second two-position three-way reversing valve, a T port of the first two-position two-way reversing valve is connected with a B port and an upper side control cavity of the second two-position three-way reversing valve, a right side control cavity of the first two-position two-way reversing valve is connected with an A port of the first two-position three-way reversing valve, the load sensitive system is connected with the T port of the second two-position three-way reversing valve, the P port of the second two-position three-way reversing valve is connected with an upper control cavity of the second two-position three-way reversing valve, a lower side control cavity of the first two-position three-way reversing valve and the load sensitive system are connected with the T port.
Preferably, the load sensitive system comprises: the first three-position five-way reversing valve, the second three-position five-way reversing valve, the first pressure compensation valve, the second pressure compensation valve, the shuttle valve, the second two-position two-way reversing valve, the differential pressure reducing valve and the throttling hole;
a port T of the first three-position five-way reversing valve is connected with a port T of the second three-position five-way reversing valve and the hydraulic oil tank, a port A of the first three-position five-way reversing valve is connected with a port P of the first pressure compensation valve, a port B of the first three-position five-way reversing valve is connected with a port B of the first actuator, a port C of the first three-position five-way reversing valve is connected with a port A of the shuttle valve and a left side control cavity of the first pressure compensation valve, and a port T of the first pressure compensation valve is connected with a port A of the first actuator;
the port A of the second three-position five-way reversing valve is connected with the port P of a second pressure compensation valve, the port C of the second three-position five-way reversing valve is connected with the port B of the shuttle valve and a left control cavity of the second pressure compensation valve, and the port T of the pressure compensation valve is connected with the port A of the second actuator;
the port C of the shuttle valve is connected with the port A of an orifice and a left control cavity of the second two-position two-way reversing valve, the port B of the orifice is connected with a lower control cavity of the differential pressure reducing valve, the port A of the differential pressure reducing valve is connected with the lower control cavity of the differential pressure reducing valve, the left control cavity of the first pressure compensating valve and the left control cavity of the second pressure compensating valve, and the port T of the differential pressure reducing valve are connected with the hydraulic oil tank;
the output end of the main pump is connected with the P port of the first three-position five-way reversing valve, the P port of the second three-position five-way reversing valve, the P port and the right control cavity of the second two-position two-way reversing valve, the upper side control cavity connected with the differential pressure reducing valve, the right side control cavity of the first pressure compensating valve and the right side control cavity of the second pressure compensating valve.
The left control cavity of the second two-position two-way reversing valve is connected with a port P of the second two-position three-way reversing valve;
and a port A of the differential pressure reducing valve is connected with an upper control cavity of the first two-position three-way reversing valve.
The invention provides an engineering mechanical device, which comprises the novel load rotating speed dual-sensing system.
A third embodiment of the present invention provides a control method for an engineering mechanical device based on the foregoing, including:
detecting a maximum pressure value of a load and an outlet pressure value of a main pump source;
and controlling the difference value between the maximum pressure value of the load and the outlet pressure value of the main pump source to be a preset value through a rotating speed sensitive valve group based on the rotating speed of the power source.
Preferably, the difference between the maximum pressure value of the load and the outlet pressure value of the main pump source is controlled to be a preset value by a rotation speed sensitive valve based on the rotation speed of the power source, specifically:
when the power source is detected to be in low-speed operation, the target control pressure difference between the outlet pressure of the main pump and the maximum load pressure is reduced, so that the pressure difference of a throttling opening of the rotating speed sensitive valve group is reduced, and the corresponding proportional relation of the oil supply flow of the system, the pilot signal and the target flow is reduced, so that the control precision of the pilot signal on the target flow is improved.
Preferably, the difference between the maximum pressure value of the load and the outlet pressure value of the main pump source is controlled to be a preset value by a rotation speed sensitive valve based on the rotation speed of the power source, specifically:
when the power source is detected to be in high-speed operation, the target control pressure difference between the outlet pressure of the main pump and the maximum load pressure is increased, so that the pressure difference of a throttling opening of the rotating speed sensitive valve group is increased, and the corresponding proportional relation of the oil supply flow, the pilot signal and the target flow of the system is improved, so that the action speed of the system is increased.
Based on the novel load rotating speed double-sensing system, the engineering mechanical device and the control method thereof, the flow matching of a hydraulic pump is realized by detecting the maximum load pressure, the difference value between the outlet pressure of a main pump and the maximum load pressure is controlled to be a certain control value, meanwhile, the control value is controlled by a rotating speed sensitive valve group based on the rotating speed of a power source, and under the condition that the power source runs at low speed, the target control pressure difference between the outlet pressure of the hydraulic pump and the maximum load pressure is reduced, so that the pressure difference of a throttling port of the rotating speed sensitive valve group is reduced, the corresponding proportional relation of the oil supply flow of a system, a pilot signal and the target flow is reduced, and the control precision of the pilot signal on the target flow is improved. Under the condition that a power source runs at a high speed, the target control pressure difference between the outlet pressure of the main pump and the maximum load pressure is increased, so that the pressure difference of a throttling port of the rotating speed sensitive valve group is increased, the corresponding proportional relation of the oil supply flow, the pilot signal and the target flow of the system and the through-flow capacity of the unit opening of the throttling valve port are improved, and the action speed of the system is further improved.
Drawings
FIG. 1 is a schematic structural diagram of a novel load rotation speed dual-sensing system provided by the invention;
fig. 2 is a schematic flow chart of a control method of a construction machine according to the present invention.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present invention more apparent, the technical solutions of the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings of the embodiments of the present invention, and it is obvious that the described embodiments are some, but not all embodiments of the present invention. All other embodiments, which can be obtained by a person skilled in the art without any inventive step based on the embodiments of the present invention, are within the scope of the present invention. Thus, the following detailed description of the embodiments of the present invention, as presented in the figures, is not intended to limit the scope of the invention, as claimed, but is merely representative of selected embodiments of the invention. All other embodiments, which can be obtained by a person skilled in the art without inventive efforts based on the embodiments of the present invention, are within the scope of protection of the present invention.
The following detailed description of specific embodiments of the invention refers to the accompanying drawings.
The invention discloses a novel load rotating speed double-sensing system, an engineering mechanical device and a control method thereof, aiming at solving the problem that the same pressure difference cannot simultaneously give consideration to the wide-stroke control of a fine operation process and the large-flow output requirement of a rapid operation process.
Referring to fig. 1, a first embodiment of the present invention provides a novel load rotation speed dual sensing system, which includes: the system comprises a main pump source, a pilot pump 3, a rotating speed sensitive valve bank, a load sensitive system, a first actuator 13 and a second actuator 14;
the main pump source is connected with the first actuator 13 and the second actuator 14 through the load sensitive system, the main pump source is coaxially connected with the pilot pump 3, and the pilot pump 3 is connected with the main pump source and the load sensitive system through the rotating speed sensitive valve bank;
the rotating speed sensitive valve group is configured to monitor the rotating speed of a main pump source and adjust the target control pressure difference of the load sensitive system according to the rotating speed of the main pump source.
Preferably, the main pump source includes: the device comprises a power source 1, a main pump 2, a first two-position three-way reversing valve 8, a first displacement adjusting mechanism 7 and a second displacement adjusting mechanism 6;
the output shaft of power supply 1 with 2 machinery of main pump link to each other, the input of main pump 2 is used for being connected with hydraulic tank, the control mouth of the first discharge adjustment mechanism 7 of output of main pump 2 is connected, the B mouth of first two-position three-way switching-over valve 8 with hydraulic tank connects, the P mouth of first two-position three-way switching-over valve 8 second discharge adjustment mechanism 6 is connected, the A mouth of first two-position three-way switching-over valve 8 with the sensitive valves of rotational speed is connected, the upper and lower control chamber of first two-position three-way switching-over valve 8 with the sensitive headtotail of load.
Preferably, the speed sensitive valve set comprises: a first two-position two-way reversing valve 4 and a second two-position three-way reversing valve 5;
wherein the input end of the pilot pump 3 is used for being connected with a hydraulic oil tank, the output end of the pilot pump 3 is connected with the P port and the left side control cavity of the first two-position two-way reversing valve 4 and the lower side control cavity of the second two-position three-way reversing valve 5, the T port of the first two-position two-way reversing valve 4 is connected with the B port and the upper side control cavity of the second two-position three-way reversing valve 5, the right side control cavity of the first two-position two-way reversing valve 4, the A port of the first two-position three-way reversing valve 8 and the load sensitive system, and the port A of the second two-position three-way reversing valve 5 is connected with the hydraulic oil tank, and the port P of the second two-position three-way reversing valve 5 is connected with the upper control cavity of the second two-position three-way reversing valve 5, the lower side control cavity of the first two-position three-way reversing valve 8 and the load sensitive system.
Preferably, the load sensitive system comprises: a first three-position five-way reversing valve 9, a second three-position five-way reversing valve 10, a first pressure compensation valve 11, a second pressure compensation valve 12, a shuttle valve 15, a second two-position two-way reversing valve 16, a differential pressure reducing valve 17 and an orifice 18;
a port T of the first three-position five-way reversing valve 9 is connected with a port T of the second three-position five-way reversing valve 10 and the hydraulic oil tank, a port A of the first three-position five-way reversing valve 9 is connected with a port P of the first pressure compensation valve 11, a port B of the first three-position five-way reversing valve 9 is connected with a port B of the first actuator 13, a port C of the first three-position five-way reversing valve 9 is connected with a port A of the shuttle valve 15 and a left side control cavity of the first pressure compensation valve 11, and a port T of the first pressure compensation valve 11 is connected with a port A of the first actuator 13;
a port A of the second three-position five-way reversing valve 10 is connected with a port P of a second pressure compensation valve 12, a port C of the second three-position five-way reversing valve 10 is connected with a port B of the shuttle valve 15 and a left control cavity of the second pressure compensation valve 12, and a port T of the pressure compensation valve is connected with a port A of the second actuator 14;
the port C of the shuttle valve 15 is connected with the port a of an orifice 18 and the left control cavity of the second two-position two-way reversing valve 16, the port B of the orifice 18 is connected with the lower control cavity of the differential pressure reducing valve 17, the port a of the differential pressure reducing valve 17 is connected with the lower control cavity of the differential pressure reducing valve 17, the left control cavity of the first pressure compensating valve 11 and the left control cavity of the second pressure compensating valve 12, and the port T of the differential pressure reducing valve 17 are connected with the hydraulic oil tank;
the output end of the main pump 2 is connected with the port P of the first three-position five-way reversing valve 9, the port P of the second three-position five-way reversing valve 10, the port P and the right control cavity of the second two-position two-way reversing valve 16, the upper side control cavity connected with the differential pressure reducing valve 17, the right side control cavity of the first pressure compensating valve 11 and the right side control cavity of the second pressure compensating valve 12.
The left control cavity of the second two-position two-way reversing valve 16 is connected with a port P of the second two-position three-way reversing valve 5;
and a port P of the differential pressure reducing valve 17 is connected with a port T of the first two-position two-way reversing valve 4, and a port A of the differential pressure reducing valve 17 is connected with an upper control cavity of the first two-position three-way reversing valve 8.
With continued reference to fig. 1, the following description will explain the specific working principle of the present invention:
after the engineering machinery is started, an operator can adjust the throttle opening according to the earthwork operation requirement, and the power source 1 drives the main pump 2 and the pilot pump 3 to respectively supply oil to the load sensitive system and the pilot oil way according to the target throttle rotating speed. When the input of the pilot handle of the engineering machinery is not input or is lower than a control threshold value, the first three-position five-way reversing valve 9 and the second three-position five-way reversing valve 10 are positioned at the middle positions, hydraulic oil of the main pump 2 flows into the second two-position two-way reversing valve 16, at the moment, a port 15A, B of the shuttle valve is connected with an oil tank, the pressure of a port C is approximate to zero, and the pressure of an outlet of the main pump 2 is stabilized to be spring control pressure of the second two-position two-way reversing valve 16 through dynamic adjustment of the second two-position two-way reversing valve 16. Meanwhile, high-pressure oil generated by the pilot pump 3 flows into the first two-position two-way reversing valve 4, and respectively flows into the first two-position three-way reversing valve 8A port and the upper and lower control cavities of the first two-position three-way reversing valve 8 after being dynamically adjusted by the second two-position three-way reversing valve 5 and the second two-position two-way reversing valve 16, so that pressure oil with the pressure close to that of the outlet of the main pump 2 is generated to control the first displacement adjusting mechanism 7, the displacement of the main pump 2 is reduced, the minimum oil supply displacement of the system leakage is ensured, and the system energy consumption in the non-action process of the system is reduced.
When a signal higher than a control threshold value is input by a pilot handle (not shown) of the engineering machinery, the system controls the opening degrees of valve ports of a first three-position five-way reversing valve 9 and a second three-position five-way reversing valve 10 according to the linear relation of the input signal of the pilot handle (not shown), and simultaneously, the system controls a power source 1 to drive a main pump 2 and a pilot pump 3 to respectively supply oil for a load sensitive system and a pilot oil way according to a target throttle signal. High-pressure oil generated by the main pump 2 flows into a corresponding first actuator 13 and a corresponding second actuator 14 through the first three-position five-way reversing valve 9, the second three-position five-way reversing valve 10, the first pressure compensation valve 11 and the second pressure compensation valve 12. The pilot pump 3 generates hydraulic oil to flow into a speed sensitive valve and a pressure difference reducing valve 17 which are composed of a first two-position two-way reversing valve 4 and a second two-position three-way reversing valve 5, target pressure oil is generated to be used for controlling the discharge capacity of the main pump 2, the outlet pressure of the main pump 2 is controlled through the volume adjustment of the main pump 2 to be only higher than the maximum load pressure by a target value, and the target value is equal to the hydraulic oil pressure generated after the hydraulic oil generated by the pilot pump 3 flows into the speed sensitive valve and the pressure difference reducing valve 17 which are composed of the first two-position two-way reversing valve 4 and the second two-position three-way reversing valve 5. For different rotating speeds of the power source 1, the displacement of the pilot pump 3 is fixed, the output flows of the pilot pump 3 are different due to different rotating speeds, when the rotating speed of the power source 1 is higher, more flows are generated by the pilot pump 3 and flow into the first two-position two-way reversing valve 4, smaller pressure difference is generated and flows out of the first two-position two-way reversing valve 4 through dynamic balance adjustment of a throttling hole 18 structure of the first two-position two-way reversing valve 4, the outlet pressure of the first two-position two-way reversing valve 4 is higher, and the pressure flows into an opening of the first two-position three-way reversing valve 8A and an upper control cavity and a lower control cavity of the first two-position three-way reversing valve 8 through the second two-position three-way reversing valve 5 and a pressure difference pressure reducing valve 17 to adjust the displacement of the main pump 2, so that the difference between the outlet pressure of the main pump 2 and the maximum load pressure of the system is equal to the outlet pressure of the first two-position two-way reversing valve 4, and the pressure value is higher. When the rotating speed of the power source 1 is low, the pilot pump 3 generates less flow and flows into the first two-position two-way reversing valve 4, a large pressure difference is generated through dynamic balance adjustment through a throttling hole 18 structure of the first two-position two-way reversing valve 4 and flows out of the first two-position two-way reversing valve 4, so that the outlet pressure of the first two-position two-way reversing valve 4 is small, the pressure flows into an opening of the first two-position three-way reversing valve 8A and an upper control cavity and a lower control cavity of the first two-position three-way reversing valve 8 through the second two-position three-way reversing valve 5 and a pressure difference reducing valve 17, the displacement of the main pump 2 is adjusted, the difference value between the outlet pressure of the main pump 2 and the maximum load pressure of the system is equal to the outlet pressure of the first two-position two-way reversing valve 4, and the pressure value is small. The corresponding relation of the valve core and the flow of the main valve under different pressure differences is changed by controlling the difference between the outlet pressure of different pumps and the maximum load pressure of a system, so that the input of a throttle signal of the whole engine is smaller during fine action, the rotating speed of a power source 1 is lower, a smaller output pressure value is generated by a rotating speed sensitive valve consisting of a first two-position two-way reversing valve 4 and a second two-position three-way reversing valve 5, the pressure difference value between the outlet pressure of the main pump 2 and the maximum load pressure is controlled to be smaller, the input signal and the system flow regulation have better linear control precision, the input of the throttle signal of the whole engine is larger during fast action, the rotating speed of the power source 1 is higher, a larger output pressure value is generated by a rotating speed sensitive valve consisting of the first two-position two-way reversing valve 4 and the second two-position three-way reversing valve 5, and the pressure value between the outlet pressure of the main pump 2 and the maximum load pressure is controlled to be larger, the flow regulating range of the input signal corresponding to the system is wider, and the system has higher action speed. And then through the mode, the system rotating speed sensitive control under different rotating speeds of the power source 1 is realized.
In the working process of the system, pressure oil generated by the pilot pump 3 flows into a port P of the differential pressure reducing valve 17 after being regulated by the first two-position two-way reversing valve 4, flows out of a port A of the differential pressure reducing valve 17, is fed back to a control cavity below the differential pressure reducing valve 17, and is used for regulating the discharge capacity of the main pump 2. And the upper control cavity of the differential pressure reducing valve 17 is connected with the outlet of the main pump 2, the lower control cavity of the differential pressure reducing valve 17 is connected with the port C of the shuttle valve 15 through an orifice 18, and the port 15A, B of the shuttle valve is respectively connected with the load cavities of the first actuator 13 and the second actuator 14, so that the highest working pressure cavity of the system is detected, the high-pressure oil flows out through the port C of the shuttle valve 15, is subjected to damping filtering through the orifice 18 and then is fed back to the lower control cavity of the differential pressure reducing valve 17. The pressure difference reducing valve 17 compares the outlet pressure of the main pump 2 with the maximum load pressure, and the difference value between the outlet pressure and the maximum load pressure is stabilized by the pressure difference reducing valve 17 to be equal to the outlet pressure of the first two-position two-way reversing valve 4, so that the function of low-pass filtering is achieved, the system impact caused by severe load change is reduced, and the stability of the system is improved.
When multiple actuators of the engineering machinery act simultaneously, and input values of all pilot handles (not shown) are high, at the moment, the flow generated by the main pump 2 even if the main pump works at the maximum displacement is not enough to ensure that the multiple actuators operate at the target high speed, and the system enters a flow saturation area. At this time, the main pump 2 maintains the difference between the outlet pressure and the maximum load pressure of the main pump 2 as a target value through displacement adjustment, and meanwhile, the system dynamically adjusts through the first pressure compensation valve 11 and the second pressure compensation valve 12, so that the pressure difference of the throttle ports of the first three-position five-way reversing valve 9 and the second three-position five-way reversing valve 10 is stabilized to be constant, and the pressure difference of the throttle ports of the first three-position five-way reversing valve 9 and the second three-position five-way reversing valve 10 is also enabled to be equal, and further, when the flow is saturated, the flow flowing into each actuator is distributed in equal proportion according to the areas of the throttle ports of the first three-position five-way reversing valve 9 and the second three-position five-way reversing valve 10, and the coordination of the cooperative actions of multiple actuators is ensured.
The invention provides an engineering mechanical device, which comprises the novel load rotating speed dual-sensing system.
Referring to fig. 2, a third embodiment of the present invention provides a control method for a construction machine device based on the foregoing, including:
s101, detecting the maximum pressure value of a load and the outlet pressure value of a main pump source;
and S102, controlling the difference value between the maximum pressure value of the load and the outlet pressure value of the main pump source to be a preset value through a rotating speed sensitive valve group based on the rotating speed of the power source 1.
Preferably, the difference between the maximum pressure value of the load and the outlet pressure value of the main pump source is controlled to be a preset value by a rotation speed sensitive valve based on the rotation speed of the power source 1, specifically:
when the power source 1 is detected to be in low-speed operation, the target control pressure difference between the outlet pressure of the main pump 2 and the maximum load pressure is reduced, so that the throttle opening pressure difference of the rotating speed sensitive valve group is reduced, the corresponding proportional relation of the oil supply flow of the system, the pilot signal and the target flow is reduced, and the control precision of the pilot signal on the target flow is improved.
Preferably, the difference between the maximum pressure value of the load and the outlet pressure value of the main pump source is controlled to be a preset value by a rotation speed sensitive valve based on the rotation speed of the power source 1, specifically:
when the power source 1 is detected to be in high-speed operation, the target control pressure difference between the outlet pressure of the main pump 2 and the maximum load pressure is increased, so that the pressure difference of a throttling opening of the rotating speed sensitive valve group is increased, and the corresponding proportional relation of the oil supply flow, the pilot signal and the target flow of the system is improved, so that the action speed of the system is increased.
Based on the novel load rotating speed double-sensitive system, the engineering mechanical device and the control method thereof, the flow matching of the hydraulic pump is realized by detecting the maximum load pressure, the difference value between the outlet pressure of the main pump 2 and the maximum load pressure is controlled to be a certain control value, meanwhile, the control value is controlled by the rotating speed sensitive valve group based on the rotating speed of the power source 1, under the condition that the power source 1 runs at low speed, the target control pressure difference between the outlet pressure of the hydraulic pump and the maximum load pressure is reduced, the pressure difference of a throttling port of the rotating speed sensitive valve group is further reduced, the corresponding proportional relation of the oil supply flow of the system, a pilot signal and the target flow is reduced, and the control precision of the pilot signal to the target flow is improved. Under the condition that the power source 1 runs at a high speed, the target control pressure difference between the outlet pressure of the main pump 2 and the maximum load pressure is increased, the throttle opening pressure difference of the rotating speed sensitive valve group is further increased, the corresponding proportional relation of the oil supply flow, the pilot signal and the target flow of the system and the through-flow capacity of the unit opening of the throttle valve opening are improved, and the action speed of the system is further improved.
The above is only a preferred embodiment of the present invention, and the protection scope of the present invention is not limited to the above-mentioned embodiments, and all technical solutions belonging to the idea of the present invention belong to the protection scope of the present invention.
Claims (8)
1. A novel load rotation speed dual-sensing system is characterized by comprising: the system comprises a main pump source, a pilot pump, a rotating speed sensitive valve group, a load sensitive system, a first actuator and a second actuator;
the main pump source is connected with the first actuator and the second actuator through the load sensitive system, the main pump source is coaxially connected with the pilot pump, and the pilot pump is connected with the main pump source and the load sensitive system through the rotating speed sensitive valve bank;
the rotating speed sensitive valve group is configured to monitor the rotating speed of a main pump source and adjust the target control pressure difference of the load sensitive system according to the rotating speed of the main pump source.
2. The novel load-speed dual sensing system of claim 1, wherein the primary pump source comprises: the system comprises a power source, a main pump, a first two-position three-way reversing valve, a first displacement adjusting mechanism and a second displacement adjusting mechanism;
the output shaft of power supply with the main pump machinery links to each other, the input of main pump is used for being connected with hydraulic tank, the control mouth of the first discharge capacity adjustment mechanism of output of main pump is connected, the B mouth of first two-position tee bend switching-over valve with hydraulic tank connects, the P mouth of first two-position tee bend switching-over valve second discharge capacity adjustment mechanism connects, the A mouth of first two-position tee bend switching-over valve with the sensitive valves of rotational speed is connected, the upper and lower control chamber of first two-position tee bend switching-over valve with the sensitive headtotail of load.
3. The novel load-speed dual-sensing system as claimed in claim 2, wherein the speed-sensing valve set comprises: a first two-position two-way reversing valve and a second two-position three-way reversing valve;
the input end of the pilot pump is used for being connected with a hydraulic oil tank, the output end of the pilot pump is connected with a P port and a left side control cavity of the first two-position two-way reversing valve, a lower side control cavity of the second two-position three-way reversing valve, a T port of the first two-position two-way reversing valve is connected with a B port and an upper side control cavity of the second two-position three-way reversing valve, a right side control cavity of the first two-position two-way reversing valve is connected with an A port of the first two-position three-way reversing valve, the load sensitive system is connected with the T port of the second two-position three-way reversing valve, the P port of the second two-position three-way reversing valve is connected with an upper control cavity of the second two-position three-way reversing valve, a lower side control cavity of the first two-position three-way reversing valve and the load sensitive system are connected with the T port.
4. The novel load-speed dual sensing system of claim 3, wherein the load sensing system comprises: the system comprises a first three-position five-way reversing valve, a second three-position five-way reversing valve, a first pressure compensation valve, a second pressure compensation valve, a shuttle valve, a second two-position two-way reversing valve, a differential pressure reducing valve and a throttling hole;
a port T of the first three-position five-way reversing valve is connected with a port T of the second three-position five-way reversing valve and the hydraulic oil tank, a port A of the first three-position five-way reversing valve is connected with a port P of the first pressure compensation valve, a port B of the first three-position five-way reversing valve is connected with a port B of the first actuator, a port C of the first three-position five-way reversing valve is connected with a port A of the shuttle valve and a left side control cavity of the first pressure compensation valve, and a port T of the first pressure compensation valve is connected with a port A of the first actuator;
the port A of the second three-position five-way reversing valve is connected with the port P of a second pressure compensation valve, the port C of the second three-position five-way reversing valve is connected with the port B of the shuttle valve and a left control cavity of the second pressure compensation valve, and the port T of the pressure compensation valve is connected with the port A of the second actuator;
the port C of the shuttle valve is connected with the port A of an orifice and a left control cavity of the second two-position two-way reversing valve, the port B of the orifice is connected with a lower control cavity of the differential pressure reducing valve, the port A of the differential pressure reducing valve is connected with the lower control cavity of the differential pressure reducing valve, the left control cavity of the first pressure compensating valve and the left control cavity of the second pressure compensating valve, and the port T of the differential pressure reducing valve are connected with the hydraulic oil tank;
the output end of the main pump is connected with the P port of the first three-position five-way reversing valve, the P port of the second three-position five-way reversing valve, the P port and the right control cavity of the second two-position two-way reversing valve, the upper side control cavity connected with the differential pressure reducing valve, the right side control cavity of the first pressure compensating valve and the right side control cavity of the second pressure compensating valve.
The left control cavity of the second two-position two-way reversing valve is connected with a port P of the second two-position three-way reversing valve;
and a port A of the differential pressure reducing valve is connected with an upper control cavity of the first two-position three-way reversing valve.
5. A construction machinery device, characterized in that, it comprises a novel load rotation speed double-sensing system as claimed in any one of claims 1 to 4.
6. The method for controlling the construction machinery device according to claim 5, comprising:
detecting a maximum pressure value of a load and an outlet pressure value of a main pump source;
and controlling the difference value between the maximum pressure value of the load and the outlet pressure value of the main pump source to be a preset value through a rotating speed sensitive valve group based on the rotating speed of the power source.
7. The method for controlling an engineering mechanical device according to claim 6, wherein the difference between the maximum pressure value of the load and the outlet pressure value of the main pump source is controlled to be a preset value by a rotation speed sensitive valve based on the rotation speed of the power source, and specifically comprises:
when the power source is detected to be in low-speed operation, the target control pressure difference between the outlet pressure of the main pump and the maximum load pressure is reduced, so that the pressure difference of a throttling opening of the rotating speed sensitive valve group is reduced, and the corresponding proportional relation of the oil supply flow of the system, the pilot signal and the target flow is reduced, so that the control precision of the pilot signal on the target flow is improved.
8. The method for controlling an engineering mechanical device according to claim 6, wherein the difference between the maximum pressure value of the load and the outlet pressure value of the main pump source is controlled to be a preset value by a rotation speed sensitive valve based on the rotation speed of the power source, and specifically comprises:
when the power source is detected to be in high-speed operation, the target control pressure difference between the outlet pressure of the main pump and the maximum load pressure is increased, so that the pressure difference of a throttling opening of the rotating speed sensitive valve group is increased, and the corresponding proportional relation of the oil supply flow, the pilot signal and the target flow of the system is improved, so that the action speed of the system is increased.
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| CN202210372145.9A CN114622618A (en) | 2022-04-11 | 2022-04-11 | Novel load rotating speed double-sensitive system, engineering mechanical device and control method thereof |
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Application publication date: 20220614 |