CN113697673A - Hydraulic control method and device and crane - Google Patents
Hydraulic control method and device and crane Download PDFInfo
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- CN113697673A CN113697673A CN202111016288.8A CN202111016288A CN113697673A CN 113697673 A CN113697673 A CN 113697673A CN 202111016288 A CN202111016288 A CN 202111016288A CN 113697673 A CN113697673 A CN 113697673A
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
- B66C13/00—Other constructional features or details
- B66C13/18—Control systems or devices
- B66C13/20—Control systems or devices for non-electric drives
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/20576—Systems with pumps with multiple pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/78—Control of multiple output members
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Automation & Control Theory (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention provides a hydraulic control method, a hydraulic control device and a crane, wherein the hydraulic control method is applied to a hydraulic system with an electric control pump and an electro-hydraulic proportional multi-way valve, and comprises the following steps: acquiring the current flow of the electric control pump and the required flow of the hydraulic actuating element; comparing the demanded flow with the current flow; and when the current flow is smaller than the required flow, adjusting the opening of a valve core of the electro-hydraulic proportional multi-way valve so as to adapt the required flow to the current flow. Compared with the existing hydraulic system consisting of the load-sensitive variable pump and the load-sensitive multi-way valve, the hydraulic system has the advantage that the probability of poor action harmony is reduced.
Description
Technical Field
The invention relates to the technical field of engineering machinery, in particular to a hydraulic control method and device and a crane.
Background
At present, a crane has various action combinations according to working condition requirements, and the crane mainly comprises action modes such as extension, main roll lifting, auxiliary roll lifting, lifting amplitude, left-right rotation and the like. However, when the flow rate is not saturated, the coordination of the operation is poor.
Disclosure of Invention
The problem to be solved by the invention is how to reduce the probability of poor action harmony when the flow is not saturated.
In order to solve the above problems, the present invention provides a hydraulic control method, which is applied to a hydraulic system having an electric control pump and an electro-hydraulic proportional multi-way valve, and comprises:
acquiring the current flow of the electric control pump and the required flow of the hydraulic actuating element;
comparing the demanded flow with the current flow;
and when the current flow is smaller than the required flow, adjusting the opening of a valve core of the electro-hydraulic proportional multi-way valve so as to adapt the required flow to the current flow.
Optionally, the obtaining the current flow rate of the electronically controlled pump includes:
acquiring the current rotating speed of an engine and the maximum flow of the electric control pump;
and obtaining the current flow of the electric control pump according to the current rotating speed and the maximum flow.
Optionally, the obtaining of the demanded flow of the hydraulic actuator includes:
acquiring position information of an operating handle;
obtaining opening information corresponding to the valve core according to the position information;
and converting the opening information into the required flow of the hydraulic actuator.
Optionally, the adjusting the opening degree of a valve element of the electro-hydraulic proportional multi-way valve to adapt the required flow rate to the current flow rate includes:
when only one hydraulic executive component works, the valve core opening corresponding to the electro-hydraulic proportional multi-way valve is adjusted, so that the required flow is adjusted to be matched with the current flow;
when at least two hydraulic executing parts work, the valve core opening degree corresponding to the electro-hydraulic proportional multi-way valve is adjusted according to the actual requirement of each hydraulic executing part, and therefore the current flow is distributed to each hydraulic executing part according to the actual requirement.
Optionally, the hydraulic control method further includes:
obtaining an allowable current value and a current value of the electric control pump;
and when the current value is larger than the allowable current value, controlling the electronic control pump to operate at the allowable current so as to control the flow of the electronic control pump.
Optionally, the obtaining the allowable current value of the electronically controlled pump includes:
acquiring parameter information of the electric control pump, wherein the parameter information comprises maximum current and minimum current;
acquiring the current post-pump pressure and allowable torque of the electronic control pump;
and obtaining the allowable current value of the electric control pump according to the maximum current, the minimum current, the allowable torque and the post-pump pressure.
Optionally, the determination formula of the allowable current value is:
I＝a+0.5×(T_Z×20π)/p×(b-a)/c；
wherein, I is an allowable current value of the electronic control pump 1, a is a minimum current of the electronic control pump 1, b is a maximum current of the electronic control pump 1, c is a flow rate of the electronic control pump 1, p is a post-pump pressure of the electronic control pump 1, and T _ Z is an allowable torque of the electronic control pump 1.
Optionally, the obtaining the current allowable torque of the electronically controlled pump includes:
acquiring the current rotating speed of the engine;
converting the current rotating speed into a corresponding allowable torque of the engine;
and multiplying the allowable torque of the engine by a regulating coefficient to obtain the current allowable torque of the electronic control pump.
The invention also provides a hydraulic control device comprising a computer readable storage medium storing a computer program and a processor, the computer program being read and executed by the processor to implement the hydraulic control method as described above.
The invention also provides a crane, which comprises an engine, an electric control pump, an electro-hydraulic proportional multi-way valve and the hydraulic control device, wherein the hydraulic control device is electrically connected with the engine, the electric control pump and the electro-hydraulic proportional multi-way valve.
Compared with the prior art, the invention has the beneficial effects that:
the invention adopts the electric control pump and the electro-hydraulic proportional multi-way valve, and when the electric control pump works, the current flow of the electric control pump and the required flow of the hydraulic actuating element are obtained; when the current flow is smaller than the required flow, the opening degree of the valve core of the electro-hydraulic proportional multi-way valve is adjusted to enable the required flow to be adaptive to the current flow, and compared with a hydraulic system formed by a load sensitive variable pump and a load sensitive multi-way valve, the hydraulic system has the advantage that the probability of poor action harmony is reduced.
Drawings
FIG. 1 is a schematic flow chart of one embodiment of a hydraulic control method of the present invention;
fig. 2 is a schematic diagram of one embodiment of a hydraulic system of a crane according to the present invention.
Description of reference numerals:
1. an electrically controlled pump; 2. an electro-hydraulic proportional multi-way valve; 21. a main rolling connection; 22. a secondary volume unit; 23. amplitude variation connection; 24. a telescopic link; 25. an oil inlet; 26. a working port; 27. a flow merging valve; 3. an engine; 4. a hydraulic control device; 5. a hydraulic actuator; 6. a pressure sensor.
Detailed Description
In order to make the aforementioned objects, features and advantages of the present invention comprehensible, embodiments accompanied with figures are described in detail below.
The reader should understand that in the description of this specification, reference to the description of the terms "one embodiment," "some embodiments," "an example," "a specific example" or "some examples," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, various embodiments or examples and features of different embodiments or examples described in this specification can be combined and combined by one skilled in the art without contradiction.
As shown in fig. 1, the hydraulic control method according to the embodiment of the present invention is applied to a hydraulic system having an electronic control pump 1 and an electro-hydraulic proportional multi-way valve 2, and includes the following steps:
s1, acquiring the current flow of the electric control pump 1 and the required flow of the hydraulic executive part 5;
s2, comparing the required flow with the current flow;
and S3, when the current flow is smaller than the required flow, adjusting the valve core opening of the electro-hydraulic proportional multi-way valve 2 to enable the required flow to be adaptive to the current flow.
Specifically, as shown in fig. 2, the hydraulic system includes an engine 3, an electro-hydraulic proportional multi-way valve 2, two electric control pumps 1, and a plurality of hydraulic actuators 5, wherein the electric control pumps 1 are electrically controlled variable plunger pumps, the engine 3 is in driving connection with the two electrically controlled variable plunger pumps, the electro-hydraulic proportional multi-way valve 2 is provided with two oil inlets 25 and four working ports 26, the two electrically controlled variable plunger pumps are respectively communicated with the corresponding oil inlets 25, and each working port 26 corresponds to a respective hydraulic actuator 5. When the engine 3 works, the two electric control variable plunger pumps supply oil to the electro-hydraulic proportional multi-way valve 2, and after the oil is regulated by the electro-hydraulic proportional multi-way valve 2, the hydraulic oil flows to the corresponding hydraulic executing piece 5.
In the embodiment, as the electric control pump 1 and the electro-hydraulic proportional multi-way valve 2 are adopted, the current flow of the electric control pump 1 and the required flow of the hydraulic actuating element 5 are obtained during working; when the current flow is greater than or equal to the required flow, the opening degree of a valve core of the electro-hydraulic proportional multi-way valve is kept unchanged; when the current flow is smaller than the required flow, the valve core opening of the electro-hydraulic proportional multi-way valve 2 is adjusted to enable the required flow to be adaptive to the current flow, and compared with a hydraulic system formed by a load sensitive variable pump and a load sensitive multi-way valve, the hydraulic system has the advantage that the probability of poor action coordination is reduced.
Optionally, the obtaining the current flow rate of the electronically controlled pump 1 includes:
acquiring the current rotating speed of the engine 3 and the maximum flow of the electric control pump 1;
and obtaining the current flow of the electric control pump 1 according to the current rotating speed and the maximum flow.
Specifically, the rotational speed of the engine 3 is monitored by a rotational speed sensor. The maximum flow rate of the electronic control pump 1 is a parameter recorded on a nameplate of the electronic control pump 1, and can be manually input and stored after the maximum flow rate of the electronic control pump 1 is obtained.
It should be understood that the electronically controlled pump 1 is driven by the engine 3, i.e. the engine 3 drives the electronically controlled pump 1 to rotate, so the rotation speed of the engine 3 is generally regarded as the rotation speed of the electronically controlled pump 1, and the flow rate of the electronically controlled pump 1 is determined by the formula:
q＝V×n×η；
wherein q is the flow of the electric control pump 1, V is the rotating speed of the electric control pump 1, n is the flow per revolution of the electric control pump 1, and η is the volumetric efficiency of the electric control pump 1.
Optionally, the acquiring the required flow of the hydraulic actuator 5 includes:
acquiring position information of an operating handle;
obtaining opening information corresponding to the valve core according to the position information;
and converting the opening information into the required flow of the hydraulic actuator 5.
Specifically, the electro-hydraulic proportional multi-way valve 2 is provided with a plurality of proportional solenoid valves, a valve core of each proportional solenoid valve is connected with an operating handle, the operating handles are different in position and can reflect the opening degree of the valve core of the corresponding proportional solenoid valve, that is, the opening degree information of the valve core is obtained, because the opening degree of the valve core and the output flow are in a linear relationship, the output flow under the current opening degree, that is, the required flow of the hydraulic actuator 5 can be obtained from a pre-stored opening degree-flow curve, and when the hydraulic actuator 5 has a plurality of hydraulic actuators, the required flow at the position is the sum of the required flows of the plurality of hydraulic actuators 5.
Optionally, the adjusting the opening degree of the valve element of the electro-hydraulic proportional multi-way valve 2 to adapt the required flow rate to the current flow rate includes:
when only one hydraulic executive component 5 works, the valve core opening corresponding to the electro-hydraulic proportional multi-way valve 2 is adjusted, so that the required flow is adjusted to be matched with the current flow;
when at least two hydraulic actuators 5 work, the valve core opening degree corresponding to the electro-hydraulic proportional multi-way valve 2 is adjusted according to the actual requirement of each hydraulic actuator 5, and therefore the current flow is distributed to each hydraulic actuator 5 according to the actual requirement.
Specifically, the crane has a single action and multiple combined actions according to the requirement of the working condition, such as extension, main roll lifting, auxiliary roll lifting, lifting amplitude, left-right rotation and the like, and in one embodiment, when the crane performs a single action (such as left-right rotation), if the flow of the electric control pump 1 is sufficient, the valve core opening of the corresponding proportional solenoid valve does not need to be changed. If the flow of the electronic control pump 1 is insufficient, the valve core opening degree of the corresponding proportional solenoid valve needs to be reduced, so as to adjust the required flow to match the current flow, for example, the required flow of the hydraulic actuator 5 is adjusted to be equal to or slightly larger than or slightly smaller than the current flow of the electronic control pump 1. In another embodiment, when the crane performs two combined operations (e.g., left-right rotation + main roll up and down), if the flow rate of the electronically controlled pump 1 is sufficient, it is not necessary to change the valve element opening of the corresponding proportional solenoid valve. If the flow of the electric control pump 1 is insufficient, the corresponding valve core opening degree needs to be adjusted according to the actual requirements of different hydraulic actuators 5, so that the current flow of the electric control pump 1 is distributed to different hydraulic actuators 5 according to the actual requirements, for example, the power requirement of left-right rotation is greater than that of main roll lifting, the flow distributed to the hydraulic actuator 5 performing left-right rotation is greater than that of the hydraulic actuator 5 performing main roll lifting, and the coordination of the actions is ensured.
Optionally, the hydraulic control method further includes:
obtaining an allowable current value and a current value of the electric control pump 1;
and when the current value is larger than the allowable current value, controlling the electronic control pump 1 to operate at the allowable current so as to control the flow of the electronic control pump 1.
Specifically, the current value of the electronically controlled pump 1 is obtained by the current detection circuit, and the opening degree of the electronically controlled pump 1 can be changed by changing the current value thereof, so as to adjust the flow rate thereof.
Optionally, the obtaining the allowable current value of the electronically controlled pump 1 includes:
acquiring parameter information of the electric control pump 1, wherein the parameter information comprises maximum current and minimum current;
acquiring the current post-pump pressure and allowable torque of the electronic control pump 1;
and obtaining the allowable current value of the electronic control pump 1 according to the maximum current, the minimum current, the allowable torque and the post-pump pressure.
In particular, the maximum current and the minimum current of the electronically controlled pump 1 are also parameters recorded on its name plate. After the maximum current and the minimum current of the electronic control pump 1 are obtained, the maximum current and the minimum current can be manually input for storage. Wherein, the determination formula of the allowable current value is as follows:
I＝a+0.5×(T_Z×20π)/p×(b-a)/c；
wherein, I is an allowable current value of the electronic control pump 1, a is a minimum current of the electronic control pump 1, b is a maximum current of the electronic control pump 1, c is a flow rate of the electronic control pump 1, p is a post-pump pressure of the electronic control pump 1, and T _ Z is an allowable torque of the electronic control pump 1.
The torque of the electric control pump 1 can be matched with the torque of the engine 3 by regulating and controlling the current of the electric control pump 1, the power of the engine 3 is fully utilized, and the heavy-load operation speed is further improved.
Meanwhile, when the whole hydraulic system works, in order to prevent the engine 3 from stalling, the electric control pump 1 is controlled to reduce the flow to a very small flow by changing the current before the crane is lifted to the maximum angle. Specifically, the pressure cutoff function is simulated, and when the pressure of the electronic control pump 1 reaches the maximum pressure of the system, the flow rate of the electronic control pump 1 is reduced to the minimum flow rate by changing the current, so that the flow rate of the electronic control pump 1 can be changed by controlling the current of the electronic control pump 1 during heavy-load operation, and the engine 3 is prevented from stalling.
Optionally, the obtaining the current allowable torque of the electronically controlled pump 1 includes:
acquiring the current rotating speed of the engine 3;
converting the current rotation speed into a corresponding allowable torque of the engine 3;
and multiplying the allowable torque of the engine 3 by a regulating coefficient to obtain the current allowable torque of the electronic control pump.
Specifically, the engine 3 has different torques at different rotation speeds, and after the current rotation speed of the engine 3 is obtained, the corresponding allowable torque of the engine 3 is obtained through a prestored rotation speed-allowable torque curve of the engine 3. Meanwhile, the rotation speed of the engine 3 is linearized in three sections according to 600-. After the engine allowable torque is obtained, the current allowable torque of the electronic control pump 1 can be obtained by multiplying the engine allowable torque by the corresponding regulating coefficient. For example, the engine 3 has a rotation speed of 1000r/min, and the corresponding engine 3 has an allowable torque of 2174Nm, and the corresponding electronically controlled pump 1 has an allowable torque of 1739.2 Nm.
The hydraulic control apparatus 4 according to another embodiment of the present invention includes a computer-readable storage medium storing a computer program and a processor, and the computer program is read by the processor and executed to implement the hydraulic control method as described above.
The crane in the further embodiment of the invention comprises an engine 3, an electric control pump 1, an electro-hydraulic proportional multi-way valve 2 and the hydraulic control device 4, wherein the hydraulic control device 4 is electrically connected with the engine 3, the electric control pump 1 and the electro-hydraulic proportional multi-way valve 2.
In the embodiment, the engine 3 is in driving connection with the electric control pump 1, the electro-hydraulic proportional multi-way valve 2 is provided with an oil inlet 25 and a plurality of working ports 26, the electric control pump 1 is communicated with the oil inlet 25, each working port 26 corresponds to a respective hydraulic actuator 5, the hydraulic actuators 5 can be hydraulic motors, hydraulic cylinders and the like, and the hydraulic control device 4 is electrically connected with the engine 3, the electric control pump 1 and the electro-hydraulic proportional multi-way valve 2 and is used for acquiring the current flow of the electric control pump 1 and the required flow of the hydraulic actuators 5; when the current flow is smaller than the required flow, the valve core opening of the electro-hydraulic proportional multi-way valve 2 is adjusted to enable the required flow to be adaptive to the current flow, and the electro-hydraulic proportional multi-way valve is also used for managing the flow of the electric control pump 1.
In this embodiment, the crane further includes a pressure sensor 6 disposed on a pipeline between the electric control pump 1 and the electro-hydraulic proportional multi-way valve 2, and the pressure sensor 6 is electrically connected to the hydraulic control device 4 and is used for detecting the post-pump pressure of the electric control pump 1 in real time.
As shown in fig. 2, the hydraulic system of the crane comprises a hydraulic control device 4, an engine 3, an electro-hydraulic proportional multi-way valve 2, two electric control pumps 1 and a plurality of hydraulic actuators 5, wherein the engine 3 is in driving connection with the two electric control pumps 1, the electro-hydraulic proportional multi-way valve 2 is provided with two oil inlets 25 and four working ports 26, one of the oil inlets 25 is sequentially communicated with a main rolling connector 21 and an auxiliary rolling connector 22, the other oil inlet 25 is sequentially communicated with a variable amplitude connector 23 and a telescopic connector 24, and the auxiliary rolling connector 22 is communicated with the variable amplitude connector 23 through a confluence valve 27. When the confluence valve 27 is disconnected, one of the electric control pumps 1 respectively supplies oil to the main winding hydraulic motor and the auxiliary winding hydraulic motor through the main winding coupling 21 and the auxiliary winding coupling 22, so that the actions of main winding and hook dropping can be realized, and the actions of auxiliary winding and hook dropping can also be realized; the other electric control pump 1 respectively supplies oil to the amplitude-variable hydraulic cylinder and the telescopic hydraulic cylinder through the amplitude-variable link 23 and the telescopic link 24, so that amplitude starting and amplitude falling actions can be realized, and arm extending and arm retracting actions can also be realized. At the moment, if the two electric control pumps 1 work simultaneously, various composite actions such as main coiling, amplitude variation and the like can be realized.
When the flow merging valve 27 of the multi-way valve is switched on, the two electric control pumps 1 jointly supply oil to the main winding hydraulic motor, the auxiliary winding hydraulic motor, the amplitude-variable hydraulic cylinder and the telescopic hydraulic cylinder, so that the actions of main winding-up hook and falling hook, auxiliary winding-up hook and falling hook, amplitude-variable and falling amplitude, arm extending and arm retracting and quick movement of an actuating mechanism can be realized.
In other embodiments, the electronically controlled pump 1 is changed from two to one, either eliminating the confluence valve 27 or employing pre-valve compensation.
Although the present disclosure has been described above, the scope of the present disclosure is not limited thereto. Various changes and modifications may be effected therein by one of ordinary skill in the pertinent art without departing from the spirit and scope of the present disclosure, and these changes and modifications are intended to be within the scope of the present disclosure.
Claims (10)
1. A hydraulic control method is applied to a hydraulic system with an electric control pump and an electro-hydraulic proportional multi-way valve, and is characterized by comprising the following steps:
acquiring the current flow of the electric control pump and the required flow of the hydraulic actuating element;
comparing the demanded flow with the current flow;
and when the current flow is smaller than the required flow, adjusting the opening of a valve core of the electro-hydraulic proportional multi-way valve so as to adapt the required flow to the current flow.
2. The hydraulic control method of claim 1, wherein the obtaining the current flow rate of the electronically controlled pump comprises:
acquiring the current rotating speed of an engine and the maximum flow of the electric control pump;
and obtaining the current flow of the electric control pump according to the current rotating speed and the maximum flow.
3. The hydraulic control method according to claim 1, wherein the acquiring the required flow rate of the hydraulic actuator includes:
acquiring position information of an operating handle;
obtaining opening information corresponding to the valve core according to the position information;
and converting the opening information into the required flow of the hydraulic actuator.
4. The hydraulic control method of claim 1, wherein the adjusting the spool opening of the electro-hydraulic proportional multi-way valve to adapt the demanded flow and the current flow comprises:
when only one hydraulic executive component works, the valve core opening corresponding to the electro-hydraulic proportional multi-way valve is adjusted, so that the required flow is adjusted to be matched with the current flow;
when at least two hydraulic executing parts work, the valve core opening degree corresponding to the electro-hydraulic proportional multi-way valve is adjusted according to the actual requirement of each hydraulic executing part, and therefore the current flow is distributed to each hydraulic executing part according to the actual requirement.
5. The hydraulic control method according to any one of claims 1 to 4, characterized by further comprising:
obtaining an allowable current value and a current value of the electric control pump;
and when the current value is larger than the allowable current value, controlling the electronic control pump to operate at the allowable current so as to control the flow of the electronic control pump.
6. The hydraulic control method according to claim 5, wherein the obtaining of the allowable current value of the electrically controlled pump includes:
acquiring parameter information of the electric control pump, wherein the parameter information comprises maximum current and minimum current;
acquiring the current post-pump pressure and allowable torque of the electronic control pump;
and obtaining the allowable current value of the electric control pump according to the maximum current, the minimum current, the allowable torque and the post-pump pressure.
7. The hydraulic control method according to claim 6, characterized in that the allowable current value is determined by the formula:
I＝a+0.5×(T_Z×20π)/p×(b-a)/c；
wherein, I is an allowable current value of the electronic control pump 1, a is a minimum current of the electronic control pump 1, b is a maximum current of the electronic control pump 1, c is a flow rate of the electronic control pump 1, p is a post-pump pressure of the electronic control pump 1, and T _ Z is an allowable torque of the electronic control pump 1.
8. The hydraulic control method according to claim 6, wherein the acquiring of the currently allowable torque of the electrically controlled pump includes:
acquiring the current rotating speed of the engine;
converting the current rotating speed into a corresponding allowable torque of the engine;
and multiplying the allowable torque of the engine by a regulating coefficient to obtain the current allowable torque of the electronic control pump.
9. A hydraulic control apparatus comprising a computer-readable storage medium storing a computer program and a processor, the computer program being read and executed by the processor to implement the hydraulic control method according to any one of claims 1 to 8.
10. A crane comprising an engine, an electrically controlled pump, an electro-hydraulic proportional multi-way valve and a hydraulic control device as claimed in claim 9, said hydraulic control device being electrically connected to said engine, said electrically controlled pump and said electro-hydraulic proportional multi-way valve.
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| CN203516249U (en) * | 2013-09-02 | 2014-04-02 | 安徽两淮科力机械制造有限责任公司 | Load-sensitive feedback control system for top drive drilling machine hydraulic pump station |
| CN204572637U (en) * | 2015-04-24 | 2015-08-19 | 长安大学 | Adopt the construction machinery hydraulic system of load-sensitive |
| CN109695599A (en) * | 2019-01-31 | 2019-04-30 | 广西柳工机械股份有限公司 | Variable delivery hydraulic system, pump output flow control method, engineering machinery |
| CN112746996A (en) * | 2019-10-31 | 2021-05-04 | 中联重科股份有限公司 | Load sensitive system and engineering hoisting machinery |
| CN111963505A (en) * | 2020-07-22 | 2020-11-20 | 中联重科股份有限公司 | Hydraulic system combination action control method and device and engineering machinery |
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