CN115110596B - Hydraulic control system - Google Patents
Hydraulic control system Download PDFInfo
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- CN115110596B CN115110596B CN202210885238.1A CN202210885238A CN115110596B CN 115110596 B CN115110596 B CN 115110596B CN 202210885238 A CN202210885238 A CN 202210885238A CN 115110596 B CN115110596 B CN 115110596B
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- 230000009471 action Effects 0.000 claims abstract description 21
- 230000001105 regulatory effect Effects 0.000 claims description 35
- 230000001276 controlling effect Effects 0.000 claims description 13
- 230000003750 conditioning effect Effects 0.000 claims 7
- 238000010276 construction Methods 0.000 abstract description 11
- 238000005265 energy consumption Methods 0.000 abstract description 5
- 239000002699 waste material Substances 0.000 abstract description 5
- 239000003921 oil Substances 0.000 description 107
- 238000006073 displacement reaction Methods 0.000 description 14
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 description 12
- 230000008859 change Effects 0.000 description 11
- 238000010438 heat treatment Methods 0.000 description 6
- 229910052757 nitrogen Inorganic materials 0.000 description 6
- 238000010586 diagram Methods 0.000 description 5
- 239000000446 fuel Substances 0.000 description 5
- 238000000034 method Methods 0.000 description 5
- 230000008569 process Effects 0.000 description 5
- 230000009286 beneficial effect Effects 0.000 description 3
- 230000009467 reduction Effects 0.000 description 3
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
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- 238000005516 engineering process Methods 0.000 description 1
- 239000010729 system oil Substances 0.000 description 1
Classifications
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F3/00—Dredgers; Soil-shifting machines
- E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
- E02F3/96—Dredgers; Soil-shifting machines mechanically-driven with arrangements for alternate or simultaneous use of different digging elements
- E02F3/966—Dredgers; Soil-shifting machines mechanically-driven with arrangements for alternate or simultaneous use of different digging elements of hammer-type tools
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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
-
- 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
- E02F9/2289—Closed circuit
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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
- F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
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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
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mining & Mineral Resources (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The application discloses hydraulic control system, including the work end, the master control valves, the guide operating unit, the hydraulic pump, target pressure control unit, target power control unit and controller, guide operating unit links to each other and is used for sending actuating signal to the master control valves, with control work end action, the hydraulic pump is supplied with oil to the master control valves, target pressure control unit is used for carrying pump flow control signal to the hydraulic pump, target power control unit is used for carrying pump power control signal to the hydraulic pump, the controller links to each other with guide operating unit, target pressure control unit and target power control unit, the controller is used for controlling target pressure control unit and target power control unit start and close according to actuating signal. The hydraulic control system can enable the actual flow demand of the breaking hammer to be adapted to the flow provided by the oil source, so that the waste of energy consumption of the system, overheat of the system, insufficient hammer striking force and frequency are avoided, and the construction efficiency, reliability and stability of the system are improved.
Description
Technical Field
The application relates to the technical field of hydraulic control, in particular to a hydraulic control system.
Background
Engineering machinery main machine, such as excavator, is often equipped with hydraulic breaking hammer to make breaking construction.
At present, a hydraulic control system for driving a breaking hammer on a host machine generally adopts a control mode which aims at controlling only power of a hydraulic pump output flow, and defines the pressure of a breaking oil inlet path through an overflow valve in a loop, wherein a hydraulic pump output P/Q curve in the system is shown as a curve a in fig. 1. For the system, when the output power of the system is larger, the output flow rate is probably larger, and according to the load characteristic of the breaking hammer, the hammer oil inlet pressure is higher, the oil inlet pressure is circularly fluctuated and changed, the breaking striking performance is better when the oil inlet pressure is large, but the rated pressure requirements of the hammer and the system cannot be exceeded, otherwise, the damage is possible, and therefore, in the control system, if the oil source power is set too large, the loop oil inlet pressure is excessively large, an overflow valve is opened for overflow, the heating temperature of the system is excessively high, the energy consumption is wasted, and if the oil source power is set too small, the hammer inlet flow rate is insufficient, the hammer oil inlet working pressure is insufficient, and the hammer working frequency and the striking force are insufficient. In order to prevent the system from overflowing during the operation of the breaking hammer, the output pressure P and the flow Q of the system can only be controlled within the range of the area A shown in fig. 1. For a piston reciprocating hydraulic breaking hammer, the relation curve of hammer oil inlet pressure and time is shown in fig. 2, the working cycle of the piston reciprocating hydraulic breaking hammer is divided into two stages of piston stroke and piston return stroke, the stroke time is short, the piston speed is high, the load is mainly inertial load, in order to reduce the pressure drop of the hammer oil inlet path during the stroke, the hammer oil inlet needs to have large flow rate during the stroke, the power of an oil source needs to be set to be a large value at the moment, the piston return stroke needs to overcome the oil return resistance and the nitrogen pressure, the oil pressure can rise to the maximum value along with the return stroke, the speed of the piston return stroke can be reduced to zero before reversing, the required flow rate can be obviously reduced, the power requirement of the piston return stroke on the oil source is less than the power requirement of the piston return stroke and the piston return stroke in the later stage, namely the breaking hammer has the actual power requirement which is changed in the working cycle period and the power required by the piston return stroke later stage is less and the load pressure is high. In the use process of the hammer, when parameters such as the frequency of the hammer, the nitrogen pressure and the like are adjusted or the hammer is replaced by a breaking hammer of a different model, the actual power requirement of the hammer on the system can also be changed. In the working process, as the oil temperature of the hydraulic system rises, the leakage quantity of the hydraulic circuit and the hammer can be increased, if the oil source power is not correspondingly increased to improve the system supply flow, the striking force and the frequency of the hammer can be reduced, thereby influencing the construction. In addition, there are other actuators in the host system besides the breaking hammer, and the hammer and other actuators typically have different power demands on the system, and engine speed variations can also affect the output power level of the pump.
According to the above situation, various factors influence the breaking hammer and the host control system, the hammer needs to change the power, flow and oil supply pressure of the hydraulic system, and the overall performance of the system needs to be considered, but the host control system in the prior art usually only adopts a mode of controlling the power as a target and limiting the overflow pressure, so that the actual flow requirement of the hammer is difficult to adapt to the flow provided by an oil source, the system is overheated, the energy consumption of the system is wasted, or the striking force and frequency of the hammer are insufficient, thereby influencing the construction efficiency, the reliability and the working stability of the machine, and the host adapts poorly to the breaking hammer with different parameters, and meanwhile, the system is difficult to match.
Therefore, how to avoid that the actual flow requirement of the hammer cannot be adapted to the flow provided by the oil source due to only adopting the power as the target control and combining the overflow pressure limiting mode is a technical problem that needs to be solved by the person skilled in the art at present.
Disclosure of Invention
The purpose of this application is to provide a hydraulic control system, can adjust the system's work end oil feed flow to realize flow self-adaptation control, reduce the loss, improve work efficiency and reliability.
To achieve the above object, the present application provides a hydraulic control system including:
a working end;
the main control valve group is connected with the working end and used for controlling the action of the working end;
the pilot operation assembly is connected with the main control valve group and is used for sending an action signal to the main control valve group so as to control the action of the working end;
the hydraulic pump is connected with the main control valve group and is used for supplying oil to the main control valve group;
the target pressure control assembly is connected with the hydraulic pump and is used for transmitting a pump flow regulating signal to the hydraulic pump so that the hydraulic pump can regulate the output flow according to the pump flow regulating signal;
the target power control assembly is connected with the hydraulic pump and is used for transmitting a pump power adjusting signal to the hydraulic pump so that the hydraulic pump can adjust output power according to the pump power adjusting signal;
and the controller is connected with the pilot operation assembly, the target pressure control assembly and the target power control assembly and is used for receiving the action signal, controlling the opening and closing of the target pressure control assembly and the target power control assembly according to the action signal and setting the target values of the target pressure control assembly and the target power control assembly.
In some embodiments, the target pressure control assembly includes a natural element, a pressure sensing element, a target pressure setting element, and a first throttling element, wherein the control end of the natural element is connected to the controller, the inlet of the natural element is connected to the outlet of the hydraulic pump, the outlet of the natural element is connected to one end of the first throttling element, one of the control ends of the pressure sensing element, and the inlet of the pressure sensing element, the other end of the first throttling element is connected to the other control end of the pressure sensing element and the inlet of the target pressure setting element, respectively, the outlet of the pressure sensing element is connected to the signal output oil path of the target pressure control assembly, and the outlet of the target pressure setting element is connected to the signal output oil path of the target pressure control assembly and the oil tank.
In some embodiments, the target pressure control assembly further comprises a pressure limiting element connected to the signal output oil line and the tank of the target pressure control assembly.
In some embodiments, the second throttling element is arranged on an oil circuit of which the outlet of the pressure sensing element is connected with the signal output oil circuit of the target pressure control assembly, and an oil circuit of which the outlet of the target pressure setting element is connected with the signal output oil circuit of the target pressure control assembly.
In some embodiments, the system further comprises a parameter adjuster, the parameter adjuster is connected with the controller, the controller is connected with the control end of the target pressure setting element, the target pressure of the target pressure setting element is set through the parameter adjuster by the controller, the controller is connected with the control end of the target power control component, and the output signal of the target power component is adjusted through the parameter adjuster by the controller.
In some embodiments, the pressure sensing element is a two-position three-way proportional valve.
In some embodiments, the fuel cell is a two-position, two-way solenoid valve.
In some embodiments, a relief valve block is also included, the relief valve block being connected to an outlet of the hydraulic pump.
In some embodiments, the controller is connected to the control end of the relief valve block, and the rated pressure of the relief valve block is set by the parameter regulator via the controller.
In some embodiments, the system further comprises a signal receiving and regulating assembly for receiving the pump flow regulating signal and the pump power regulating signal and regulating the output flow and the output power of the hydraulic pump according to the pump flow regulating signal and the pump power regulating signal, respectively, the signal receiving and regulating assembly comprising:
the first regulator is connected with the signal output oil way of the target pressure control assembly and the hydraulic pump and is used for receiving a pump flow regulating signal so as to regulate the output flow of the hydraulic pump;
and the second regulator is connected with the target power control assembly and the hydraulic pump and is used for receiving a pump power regulating signal so as to regulate the output power of the hydraulic pump.
Compared with the background technology, the hydraulic control system provided by the embodiment of the application comprises a working end, a main control valve bank, a pilot operation assembly, a hydraulic pump, a target pressure control assembly, a target power control assembly and a controller, wherein the main control valve bank is connected with the working end, the main control valve bank is used for controlling the action of the working end, the pilot operation assembly is connected with the main control valve bank, the pilot operation assembly is used for sending an action signal to the main control valve bank so as to control the action of the working end, the hydraulic pump is connected with the main control valve bank, the hydraulic pump is used for supplying oil to the main control valve bank, the target pressure control assembly is connected with the hydraulic pump, the target pressure control assembly is used for conveying a pump flow regulation signal to the hydraulic pump, the hydraulic pump is used for regulating output flow according to the pump flow regulation signal, the target power control assembly is connected with the hydraulic pump, the target power control assembly is used for conveying a pump power regulation signal to the hydraulic pump, the controller is connected with the pilot operation assembly, the target pressure control assembly and the target power control assembly is started and closed according to the action signal, and the target value of the target pressure control assembly and the target power control assembly is set.
Specifically, the working end may be a breaking hammer, in the breaking hammer construction, when the pilot operation assembly is operated, the breaking hammer starts to act, and the controller starts the target pressure control function of the target pressure control assembly after knowing the hammer action through the pilot operation assembly, so that the maximum oil inlet load pressure of the breaking hammer is controlled by the target pressure control assembly, namely: when the oil inlet pressure of the breaking hammer is higher than the target pressure of the target pressure control assembly, the target pressure control assembly outputs a pump flow regulating signal to quickly reduce the discharge capacity of the hydraulic pump until the oil inlet pressure of the breaking hammer is reduced to be slightly higher than the target pressure of the target pressure control assembly; when the oil inlet pressure of the breaking hammer is close to or lower than the target pressure of the target pressure control assembly, the controller controls the target pressure control assembly to be closed, the pump flow regulating signal is reduced to the minimum, the displacement of the hydraulic pump is restored to the maximum, the hydraulic pump output flow is irrelevant to the pressure on the oil inlet path of the breaking hammer as long as the oil inlet pressure of the breaking hammer is lower than the target pressure of the target pressure control assembly, the hydraulic pump output flow depends on the power setting, and the controller can set the hydraulic pump power to be as high as possible through the target power control assembly as long as the load power does not exceed the maximum power provided by the hydraulic pump during the action of the hammer, so that the system can provide as much flow for the oil inlet of the breaking hammer as possible, and the overflow loss and the heating problem of the system can not be produced due to the overlarge power setting.
The hydraulic control system provided by the embodiment of the application is provided with the target pressure control component, and the target pressure control component controls the displacement mode of the hydraulic pump to control the target pressure of the oil inlet path of the breaking hammer, so that the target pressure control component and the target power control component in the system can regulate the oil inlet flow of the breaking hammer together to realize flow self-adaptive control. Compared with the traditional mode of controlling the output flow of the hydraulic pump by taking power as a target and controlling the overflow pressure limiting mode, the hydraulic control system provided by the embodiment of the application has the following beneficial effects:
firstly, the problems of overheat and waste of oil consumption of the system caused by overhigh power adjustment of the hydraulic pump when the hydraulic control system is matched with the breaking hammer are solved;
secondly, the problem of adaptability of the hydraulic control system to the change of the flow demand of the breaking hammer in the striking cycle period is solved, namely when the flow demand of the breaking hammer is large, the system can automatically control the hydraulic pump to provide large flow, and when the flow demand of the breaking hammer is small, the system can automatically control the hydraulic pump to reduce the output flow, so that the performance of the breaking hammer operation is improved;
thirdly, the problem of the variation of the striking force frequency of the breaking hammer caused by the variation of the oil temperature of the hydraulic control system in the construction process of the breaking hammer is solved, and the stability of the operation performance of the breaking hammer is improved;
fourth, solve breaking hammer in the course of using, because of adjusting breaking hammer frequency, nitrogen pressure parameter change, engine speed change caused by demand for flow or change of the system output, thus the overflow loss of the system and heating problem that may produce;
fifthly, the problem of adapting to the breaking hammers with different parameter specifications by the same host machine is solved, the problem of system overflow or poor breaking striking performance possibly caused by mismatching of power and pressure when a user replaces different breaking hammers is reduced, the operation setting is simplified, the power and pressure adjusting requirements between the breaking hammers and other actuators are met, and the overall performance of the system is improved.
In sum, the hydraulic control system provided by the embodiment of the application can enable the actual flow demand of the breaking hammer to be matched with the flow (or the output flow of the hydraulic pump) provided by an oil source, so that the waste of system energy consumption, the overheat of the system, the impact force of a hammer and the frequency are avoided, the construction efficiency, the reliability and the stability of the system are improved, the host adapts to the breaking hammer with different parameters better, and meanwhile, the system is easier to match.
Drawings
In order to more clearly illustrate the embodiments of the present application or the technical solutions in the prior art, the drawings that are required to be used in the embodiments or the description of the prior art will be briefly described below, and it is obvious that the drawings in the following description are only embodiments of the present application, and that other drawings may be obtained according to the provided drawings without inventive effort to a person skilled in the art.
FIG. 1 is a schematic diagram of a hydraulic pump load pressure versus output flow for a prior art hydraulic control system;
FIG. 2 is a graphical representation of breaking hammer oil inlet pressure versus time for a hydraulic control system of the prior art;
FIG. 3 is a schematic diagram of a hydraulic control system in an embodiment of the present application;
FIG. 4 is a graph showing the relationship between hydraulic pump load pressure and output flow of a hydraulic control system according to an embodiment of the present application;
fig. 5 is a schematic diagram of a breaking hammer oil inlet pressure versus time of a hydraulic control system according to an embodiment of the present application.
Wherein:
the hydraulic system comprises a 1-hydraulic pump, a 2-target pressure control assembly, a 3-main control valve bank, a 4-working end, a 5-controller, a 6-pilot operation assembly, a 7-target power control assembly, an 8-overflow valve bank, a 9-parameter regulator and a 10-actuator;
21-a fuel element, 22-a pressure sensing element, 23-a pressure defining element, 24-a target pressure setting element, 25-a first throttling element, 26-a second throttling element.
Detailed Description
The following description of the embodiments of the present application will be made clearly and fully with reference to the accompanying drawings, in which it is evident that the embodiments described are only some, but not all, of the embodiments of the present application. All other embodiments, which can be made by one of ordinary skill in the art without undue burden from the present disclosure, are within the scope of the present disclosure.
In order to better understand the aspects of the present application, a further detailed description of the present application will be provided below with reference to the accompanying drawings and detailed description.
Referring to fig. 3, 4 and 5, fig. 3 is a schematic diagram of a hydraulic control system according to an embodiment of the present application; FIG. 4 is a graph showing the relationship between hydraulic pump load pressure and output flow of a hydraulic control system according to an embodiment of the present application; fig. 5 is a schematic diagram of a breaking hammer oil inlet pressure versus time of a hydraulic control system according to an embodiment of the present application.
As shown in fig. 3, the hydraulic control system provided in this embodiment of the present application includes a working end 4, a master control valve group 3, a pilot operation assembly 6, a hydraulic pump 1, a target pressure control assembly 2, a target power control assembly 7 and a controller 5, where the master control valve group 3 is connected to the working end 4, the master control valve group 3 is used to control the working end 4 to operate, the pilot operation assembly 6 is connected to the master control valve group 3, the pilot operation assembly 6 is used to send an operation signal to the master control valve group 3 to control the working end 4 to operate, the hydraulic pump 1 is connected to the master control valve group 3, the hydraulic pump 1 is a system oil source, the hydraulic pump 1 is used to supply oil to the master control valve group 3, the target pressure control assembly 2 is connected to the hydraulic pump 1, the target pressure control assembly 2 is used to deliver a pump flow rate adjustment signal to the hydraulic pump 1, the target power control assembly 7 is connected to the hydraulic pump 1, the target power control assembly 7 is used to deliver a pump power adjustment signal to the hydraulic pump 1, the hydraulic pump 1 is made to adjust the output power according to the pump power adjustment signal, the controller 5 is connected to the pilot operation assembly 6, the target pressure control assembly 2 and the target power control assembly 7 is used to receive the pilot operation signal from the pilot operation assembly 6, and the target pressure control assembly 7 is set up and the target power control assembly 2 is turned off according to the target pressure control assembly 7.
Specifically, the working end 4 may be a breaking hammer, and in the construction of the breaking hammer, when the pilot operation assembly 6 is operated (the pilot operation assembly 6 may be composed of a mechanical operation valve and a sensing element or composed of an electronic operation element and an electric control valve), the breaking hammer starts to act, and the controller 5 starts the target pressure control function of the target pressure control assembly 2 after knowing the hammer action through the pilot operation assembly 6, so that the maximum oil inlet load pressure of the breaking hammer is controlled by the target pressure control assembly 2, namely: when the oil inlet pressure of the breaking hammer is higher than the target pressure of the target pressure control assembly 2, the target pressure control assembly 2 outputs a pump flow regulating signal to quickly reduce the displacement of the hydraulic pump 1 until the oil inlet pressure of the breaking hammer is reduced to be slightly higher than the target pressure of the target pressure control assembly 2; when the oil inlet pressure of the breaking hammer is close to or lower than the target pressure of the target pressure control assembly 2, the controller 5 controls the target pressure control assembly 2 to be closed, the pump flow regulating signal is reduced to the minimum, the displacement of the hydraulic pump 1 is restored to the maximum, and as long as the oil inlet pressure of the breaking hammer is lower than the target pressure of the target pressure control assembly 2, the output flow of the hydraulic pump 1 is irrelevant to the pressure on the oil inlet path of the breaking hammer, the output flow of the hydraulic pump 1 depends on the power setting, and as long as the load power during the action of the hammer does not exceed the maximum power which can be provided by the hydraulic pump 1, the controller 5 can set the power of the hydraulic pump 1 to be as high as possible through the target power control assembly 7, so that the system can provide as much flow for the oil inlet of the breaking hammer as possible, and the overflow loss and the system heating problem can not be caused by the overlarge power setting.
In addition, the hydraulic control system further comprises other actuators 10, wherein the actuators 10 are connected with the main control valve group 3, and the main control valve group 3 is used for controlling actions of the breaking hammer or other actuators 10.
The hydraulic control system provided by the embodiment of the application is provided with the target pressure control assembly 2, and the target pressure control assembly 2 controls the displacement mode of the hydraulic pump 1 to realize the target pressure control of the oil inlet path of the breaking hammer, so that the target pressure control assembly 2 and the target power control assembly 7 in the system can regulate the oil inlet flow of the breaking hammer together to realize flow self-adaptive control. Compared with the traditional mode of controlling the output flow of the hydraulic pump 1 by taking power as a target and controlling the overflow pressure limiting mode, the hydraulic control system provided by the embodiment of the application has the following beneficial effects:
firstly, the problem of overheat and waste of oil consumption of the system caused by overhigh power adjustment of the hydraulic pump 1 when the hydraulic control system is matched with the breaking hammer is solved;
secondly, the problem of adaptability of the hydraulic control system to the change of the flow demand of the breaking hammer in the striking cycle period is solved, namely when the flow demand of the breaking hammer is large, the system can automatically control the hydraulic pump 1 to provide large flow, and when the flow demand of the breaking hammer is small, the system can automatically control the hydraulic pump 1 to reduce the output flow, so that the performance of the breaking hammer operation is improved;
thirdly, the problem of the variation of the striking force frequency of the breaking hammer caused by the variation of the oil temperature of the hydraulic control system in the construction process of the breaking hammer is solved, and the stability of the operation performance of the breaking hammer is improved;
fourth, solve breaking hammer in the course of using, because of adjusting breaking hammer frequency, nitrogen pressure parameter change, engine speed change caused by demand for flow or change of the system output, thus the overflow loss of the system and heating problem that may produce;
fifthly, the problem of adapting to the breaking hammers with different parameter specifications by the same host machine is solved, the problem of system overflow or poor breaking striking performance possibly caused by mismatching of power and pressure when a user replaces different breaking hammers is reduced, the operation setting is simplified, the power and pressure adjustment requirements between the breaking hammers and other actuators 10 are met, and the overall performance of the system is improved.
In summary, the hydraulic control system provided by the embodiment of the application can enable the actual flow requirement of the breaking hammer to be matched with the flow (or the output flow of the hydraulic pump 1) provided by an oil source, so that the waste of system energy consumption, the overheat of the system, the impact force of a hammer and the frequency are avoided, the construction efficiency, the reliability and the stability of the system are improved, the host adapts to the breaking hammer with different parameters better, and meanwhile, the system is easier to match.
In some embodiments, the hydraulic control system further comprises a signal receiving and adjusting assembly for receiving the pump flow adjustment signal and the pump power adjustment signal and adjusting the output flow and the output power of the hydraulic pump 1 according to the pump flow adjustment signal and the pump power adjustment signal, respectively. Specifically, the signal receiving and adjusting assembly comprises a first regulator and a second regulator, wherein the first regulator is connected with the signal output oil way of the target pressure control assembly 2 and the hydraulic pump 1, and is used for receiving a pump flow adjusting signal so as to adjust the output flow of the hydraulic pump 1; a second regulator is connected to the target power control assembly 7 and the hydraulic pump 1, the second regulator being adapted to receive a pump power adjustment signal for adjusting the output power of the hydraulic pump 1.
In this way, the first regulator of the hydraulic pump 1 can receive the pump flow rate regulating signal output from the target pressure control assembly 2, and the stronger the output regulating signal is, the smaller the displacement of the hydraulic pump 1 will be regulated, and the second regulator of the hydraulic pump 1 receives the pump power regulating signal output from the pump target power control assembly 7 and together realizes the regulation setting of the pump power through the control of the pump displacement.
It should be noted that the signal receiving and adjusting component of the hydraulic pump 1 converts the pump flow adjusting signal and the pump power adjusting signal, and the real-time displacement of the hydraulic pump 1 is determined with a small displacement control requirement after comparison.
In some embodiments, the target pressure control assembly 2 includes a fuel element 21, a pressure sensing element 22, a target pressure setting element 24, and a first throttling element 25; wherein the control end of the natural element 21 is connected with the controller 5, the inlet of the natural element 21 is connected with the outlet of the hydraulic pump 1, and the outlet of the natural element 21 is connected with one end of the first throttling element 25, one control end of the pressure sensing element 22 and the inlet of the pressure sensing element 22; the other end of the first throttling element 25 is respectively connected with the other control end of the pressure sensing element 22 and the inlet of the target pressure setting element 24, the outlet of the pressure sensing element 22 is connected with the signal output oil circuit of the target pressure control assembly 2, and the outlet of the target pressure setting element 24 is connected with the signal output oil circuit of the target pressure control assembly 2 and the oil tank. The control from the controller 5 is received by the fuel element 21, the fuel element 21 is used for switching on or off the target pressure control function of the target pressure control assembly 2 to the system, the target pressure setting element 24 can receive the target pressure setting signal from the controller 5, and the output pressure of the signal output oil circuit of the target pressure control assembly 2 serves as the pump flow rate adjusting signal.
Of course, according to the actual needs, the pressure sensing element 22 is a two-position three-way proportional valve, the natural element 21 is a two-position two-way solenoid valve, and when the natural element 21 is in the left position, the target pressure control function of the target pressure control assembly 2 is closed, and when the natural element 21 is in the right position, the target pressure control function of the target pressure control assembly 2 is opened.
In addition, the target pressure control assembly 2 further comprises a pressure limiting element 23, the pressure limiting element 23 is connected with the signal output oil path and the oil tank of the target pressure control assembly 2, the pressure limiting element 23 is specifically an overflow valve, and the pressure limiting element 23 is used for controlling the maximum value of the output signal of the signal output oil path on the target pressure control assembly 2, so that the control stability performance is prevented from being influenced and the hydraulic pump 1 is prevented from being damaged due to the overlarge output signal.
In some embodiments, the second throttling element 26 is disposed on an oil path in which the outlet of the pressure sensing element 22 is connected to the signal output oil path of the target pressure control assembly 2, and an oil path in which the outlet of the target pressure setting element 24 is connected to the signal output oil path of the target pressure control assembly 2.
In this way, the target pressure control component 2 can sense the pressure change on the oil inlet path of the breaking hammer, when sensing that the pressure on the oil inlet path exceeds the target pressure set by the target pressure control component 2, the target pressure setting component 24 will automatically open, the acting force on the two control ends of the pressure sensing component 22 changes due to the throttling pressure difference effect of the first throttling component 25, so that the internal valve opening of the pressure sensing component 22 changes, and the size of the pump flow regulating signal output by the signal output oil path of the target pressure control component 2 is increased, the displacement of the hydraulic pump 1 is quickly reduced, the pump flow regulating signal stops increasing until the pressure on the oil inlet path of the breaking hammer is slightly higher than the target pressure, the displacement of the hydraulic pump 1 is stopped to be regulated to be small, when the pressure on the oil inlet path of the breaking hammer is close to or lower than the target pressure, the pressure setting component 2 is automatically closed, then the opening of the pressure sensing component 22 tends to be closed, the pump flow regulating signal is reduced to the minimum, the displacement of the hydraulic pump 1 is restored to the maximum, and thus the breaking hammer is controlled on the oil inlet path, namely, the maximum pressure of the breaking hammer is not required to be regulated by the hydraulic pump 1, and the target pressure is not required to be regulated on the oil inlet path.
It can be understood that the signal loop that the target pressure control assembly 2 is connected to the oil outlet of the hydraulic pump 1 is used for sensing the oil inlet load pressure when the breaking hammer works, meanwhile, the target pressure value of the target pressure control assembly 2 can be set as required, the target pressure control assembly 2 compares the target pressure value with the breaking oil inlet load pressure, when the breaking hammer oil inlet load pressure is greater than the target pressure, the target pressure control assembly 2 outputs an adjusting signal, the signal acts on the regulator of the hydraulic pump 1, and the pump regulator adjusts the displacement of the pump according to the signal so as to control the breaking hammer oil inlet pressure. In addition, the target pressure control assembly 2 has a natural function, and the load pressure of the oil inlet path of the breaking hammer can be switched on or off through the controller 5 connected with the target pressure control assembly 2 also has a function of preventing the output pressure signal of the target pressure control assembly from being overlarge, so that the control stability performance is prevented from being influenced and the hydraulic pump 1 is prevented from being damaged due to overlarge signal.
The target pressure of the target pressure control assembly 2 may be set electronically or manually by the controller 5 or by a manual adjustment lever.
In some embodiments, the hydraulic control system further comprises a parameter regulator 9, the parameter regulator 9 is connected to the controller 5, the controller 5 is connected to a control end of the target pressure setting element 24, the target pressure of the target pressure setting element 24 is set by the parameter regulator 9 via the controller 5, the controller 5 is connected to a control end of the target power control assembly 7, and the output signal of the target power assembly 7 is regulated by the parameter regulator 9 via the controller 5.
In some embodiments, the hydraulic control system further comprises a relief valve block 8, the relief valve block 8 being connected to the outlet of the hydraulic pump 1. At the same time, the control unit 5 is connected to the control end of the relief valve block 8, and the setpoint pressure of the relief valve block 8 is set by the control unit 5 via the parameter regulator 9. The relief valve group 8 can limit the maximum pressure of the outlet of the hydraulic pump 1, and the relief pressure has a multi-stage or proportional regulating function.
The controller 5 is configured to receive a breaking hammer pilot control signal (an operation signal) of the pilot operation unit 6 and a parameter adjustment signal of the parameter adjuster 9, and to set a target pressure of the target pressure control unit 2 or to turn off an adjusting action of the target pressure control unit 2 on the hydraulic pump 1 according to the signals, and to adjust and set a pump power adjustment signal of the target power control unit 7, and to set an overflow opening pressure value of the overflow valve group 8.
The following specifically describes the beneficial effects brought by the hydraulic control system provided in the embodiments of the present application.
1. In the construction process of the breaking hammer, when the pilot operation assembly 6 is operated, the breaking hammer starts to act, and meanwhile, after knowing that the breaking hammer acts through the pilot operation assembly 6, the controller 5 starts the target pressure control function of the target pressure control assembly 2, and sets the target pressure of the target pressure control assembly 2 to be lower than the set pressure of the overflow valve assembly 8 but not lower than the maximum load pressure required by the breaking hammer, so that the maximum oil inlet load pressure of the breaking hammer is controlled by the target pressure control assembly 2, namely, when the oil inlet load pressure of the breaking hammer is higher than the target pressure of the target pressure control assembly 2, the target pressure control assembly 2 outputs a pump flow regulating signal to quickly reduce the displacement of the hydraulic pump 1, so that the maximum oil inlet pressure of the breaking hammer is controlled to be slightly higher than the target pressure of the target pressure control assembly 2 but lower than the set pressure of the overflow valve assembly 8, and the output flow of the hydraulic pump 1 is determined by the power setting when the oil inlet pressure of the breaking hammer is lower than the target pressure, and as long as the maximum power provided by the pump does not exceed the maximum power provided by the pump during the operation, the controller 5 sets the maximum pump power as high as possible through the target power control assembly 7.
As shown in fig. 4, when the breaking hammer acts, the power setting of the hydraulic pump 1 can be set according to the P/Q curve c of the hydraulic pump 1, and the actual output P/Q of the hydraulic pump 1 is set according to the curve B through the target pressure control assembly 2, that is, the range of the flow supplied by the system to the breaking hammer includes the range a and the range B, so that the system can supply as much flow as possible to the oil inlet of the breaking hammer, and the overflow loss and the heating problem of the system can not be caused due to the overlarge power setting.
2. After the setting mode is adopted, when the hammer acts, the pump power can be set to be maximum because the problem of system overflow cannot occur, so that the application range of the pump to the flow supply of the hammer is improved, namely, in the working stage that the stroke and return stroke of the hammer piston are lower than the target pressure of the target pressure control assembly 2, the system can provide flow for as many hammers as possible in the maximum power range, so that the reduction or fluctuation of the oil inlet pressure in the stage is reduced, when the return stroke of the hammer piston approaches the top dead center stage, the oil inlet pressure of the hammer reaches the maximum at the moment, when the oil inlet pressure of the hammer is higher than the target pressure of the target pressure control assembly 2, the pump output flow is automatically reduced, and the actual flow of the hammer is also reduced, and the purpose that the output flow of the system is automatically adapted to the flow requirements of different stages in the working cycle period of the hammer is realized.
As shown in fig. 5, the hammer oil inlet pressure will rise to curve g when the hammer is operated due to the increase of the breaking hammer oil inlet flow rate, and at the same time, the striking performance of the breaking hammer will be improved due to the reduction of the hammer oil inlet pressure drop and the pressure fluctuation range.
3. Because the power of the hydraulic pump 1 can be set to be larger than the actual required power value of the breaking hammer, when the breaking hammer works, when the oil temperature rises to cause the increase of the leakage loss of the flow in the loop, the hammer automatically increases the absorption power, and the output flow of the hydraulic pump 1 is increased, so that the leakage loss of the oil inlet flow of the breaking hammer and the reduction of the oil inlet pressure are supplemented, the influence of the oil temperature on the frequency and the striking force of the breaking hammer can be eliminated or reduced, and the striking performance of the breaking hammer is stabilized.
4. In the use of the breaking hammer, the breaking hammer frequency is sometimes required to be regulated through a frequency modulation valve, the hammer oil inlet pressure is increased when the frequency is regulated down, the breaking hammer oil inlet demand flow is reduced, in addition, the nitrogen pressure is increased due to the temperature influence, so that the oil inlet pressure is increased, and the target pressure control component 2 limits the highest working pressure of the breaking hammer oil inlet and has the self-adaptive regulation function of the system on the flow, so that the pressure exceeding the opening pressure of an overflow valve due to the regulation of the frequency or the change of the nitrogen pressure can be avoided, and overflow loss is generated.
5. When the breaking hammer with different pressure and flow parameter requirements is matched with the same host machine, the breaking hammer and the rated pressure of the system are required, and the parameter regulator 9 is simply utilized to set the target pressure of the target pressure control assembly 2 through the controller 5, so that the maximum oil inlet pressure of the breaking hammer can meet the requirements of the breaking hammer of the model, the system power can be uniformly set to be maximum, the problem of system overflow can not occur, the application range of the host machine to the hammer is improved, and the application operation is simplified.
In addition, when the breaking hammer is operated and the breaking hammer is operated, the controller 5 senses the breaking hammer action through the pilot operation assembly 6 when the breaking hammer is also operated and the target pressure control function of the target pressure control group on the breaking hammer oil inlet is opened, meanwhile, the overflow opening pressure of the overflow valve group 8 is set to be higher than the target pressure set by the target pressure control assembly 2, at the moment, the breaking hammer oil inlet working pressure is controlled by the target pressure control assembly 2, and the flow rate is in a self-adaptive state; when other actuators 10 are operated, the controller 5 is used for closing the target pressure control function of the target pressure control assembly 2 on the system target pressure, the maximum working pressure of the pump port of the hydraulic pump 1 is controlled by the overflow valve group 8, and the system is only in a power regulation state, so that the system simultaneously meets different requirements of the breaking hammer and other actuators 10 on power and pressure.
It should be noted that in this specification relational terms such as first and second are used solely to distinguish one entity from another entity without necessarily requiring or implying any actual such relationship or order between such entities.
The hydraulic control system provided by the present application is described in detail above. Specific examples are employed herein to illustrate the principles and embodiments of the present application, and the above examples are provided only to assist in understanding the aspects of the present application and their core ideas. It should be noted that it would be obvious to those skilled in the art that various improvements and modifications can be made to the present application without departing from the principles of the present application, and such improvements and modifications fall within the scope of the claims of the present application.
Claims (9)
1. A hydraulic control system, comprising:
a working end;
the main control valve group is connected with the working end and used for controlling the action of the working end;
the pilot operation assembly is connected with the main control valve group and is used for sending an action signal to the main control valve group so as to control the action of the working end;
the hydraulic pump is connected with the main control valve group and is used for supplying oil to the main control valve group;
the target pressure control assembly is connected with the hydraulic pump and is used for conveying a pump flow regulating signal to the hydraulic pump so that the hydraulic pump can regulate output flow according to the pump flow regulating signal;
the target power control assembly is connected with the hydraulic pump and is used for transmitting a pump power adjusting signal to the hydraulic pump so that the hydraulic pump can adjust output power according to the pump power adjusting signal;
the controller is connected with the pilot operation assembly, the target pressure control assembly and the target power control assembly and is used for receiving the action signal, controlling the opening and closing of the target pressure control assembly and the target power control assembly according to the action signal and setting the target values of the target pressure control assembly and the target power control assembly;
the target pressure control assembly comprises a natural element, a pressure sensing element, a target pressure setting element and a first throttling element, wherein the control end of the natural element is connected with the controller, the inlet of the natural element is connected with the outlet of the hydraulic pump, the outlet of the natural element is connected with one end of the first throttling element, one control end of the pressure sensing element and the inlet of the pressure sensing element, the other end of the first throttling element is respectively connected with the other control end of the pressure sensing element and the inlet of the target pressure setting element, the outlet of the pressure sensing element is connected with a signal output oil circuit of the target pressure control assembly, and the outlet of the target pressure setting element is connected with a signal output oil circuit of the target pressure control assembly and an oil tank.
2. The hydraulic control system of claim 1, wherein the target pressure control assembly further comprises a pressure limiting element coupled to the signal output circuit of the target pressure control assembly and the tank.
3. The hydraulic control system according to claim 1, wherein the oil passage in which the outlet of the pressure sensing element is connected to the signal output oil passage of the target pressure control module, and the oil passage in which the outlet of the target pressure setting element is connected to the signal output oil passage of the target pressure control module are provided with a second restriction element.
4. The hydraulic control system of claim 1, further comprising a parameter regulator coupled to the controller, the controller coupled to the control end of the target pressure setting element, the target pressure of the target pressure setting element being set by the parameter regulator via the controller, the controller coupled to the control end of the target power control assembly, the output signal of the target power assembly being regulated by the parameter regulator via the controller.
5. The hydraulic control system of claim 1, wherein the pressure sensing element is a two-position three-way proportional valve.
6. The hydraulic control system of claim 1, wherein the natural element is a two-position two-way solenoid valve.
7. The hydraulic control system of claim 4, further comprising a relief valve block connected to an outlet of the hydraulic pump.
8. The hydraulic control system of claim 7, wherein the controller is coupled to a control end of the relief valve block, and wherein the nominal pressure of the relief valve block is set by the parameter regulator via the controller.
9. The hydraulic control system of any one of claims 1-8, further comprising a signal receiving and conditioning assembly for receiving the pump flow conditioning signal and the pump power conditioning signal and conditioning the output flow and output power of the hydraulic pump in accordance with the pump flow conditioning signal and the pump power conditioning signal, respectively, the signal receiving and conditioning assembly comprising:
the first regulator is connected with the signal output oil way of the target pressure control assembly and the hydraulic pump and is used for receiving the pump flow regulating signal so as to regulate the output flow of the hydraulic pump;
and a second regulator connected to the target power control assembly and the hydraulic pump for receiving the pump power adjustment signal to adjust the output power of the hydraulic pump.
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| JP2004074331A (en) * | 2002-08-13 | 2004-03-11 | Shin Caterpillar Mitsubishi Ltd | Operating fluid feed control system for breaker, and feed control method |
| CN107407300A (en) * | 2016-03-10 | 2017-11-28 | 日立建机株式会社 | Engineering machinery |
| CN107849835A (en) * | 2015-07-15 | 2018-03-27 | 斗山英维高株式会社 | The control method of engineering machinery and engineering machinery |
| WO2021046736A1 (en) * | 2019-09-11 | 2021-03-18 | 徐州徐工挖掘机械有限公司 | Hydraulic excavator control system and method |
| WO2021226791A1 (en) * | 2020-05-11 | 2021-11-18 | 徐州重型机械有限公司 | Load sensing pump system, hydraulic control system, and construction machinery |
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2022
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Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2004074331A (en) * | 2002-08-13 | 2004-03-11 | Shin Caterpillar Mitsubishi Ltd | Operating fluid feed control system for breaker, and feed control method |
| CN107849835A (en) * | 2015-07-15 | 2018-03-27 | 斗山英维高株式会社 | The control method of engineering machinery and engineering machinery |
| CN107407300A (en) * | 2016-03-10 | 2017-11-28 | 日立建机株式会社 | Engineering machinery |
| WO2021046736A1 (en) * | 2019-09-11 | 2021-03-18 | 徐州徐工挖掘机械有限公司 | Hydraulic excavator control system and method |
| WO2021226791A1 (en) * | 2020-05-11 | 2021-11-18 | 徐州重型机械有限公司 | Load sensing pump system, hydraulic control system, and construction machinery |
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