CN115110596A - Hydraulic control system - Google Patents
Hydraulic control system Download PDFInfo
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- CN115110596A CN115110596A CN202210885238.1A CN202210885238A CN115110596A CN 115110596 A CN115110596 A CN 115110596A CN 202210885238 A CN202210885238 A CN 202210885238A CN 115110596 A CN115110596 A CN 115110596A
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- 230000009471 action Effects 0.000 claims abstract description 23
- 230000001276 controlling effect Effects 0.000 claims description 11
- 230000001105 regulatory effect Effects 0.000 claims description 7
- 238000010276 construction Methods 0.000 abstract description 11
- 238000005265 energy consumption Methods 0.000 abstract description 5
- 230000003044 adaptive effect Effects 0.000 abstract description 4
- 238000013021 overheating Methods 0.000 abstract description 3
- 239000002699 waste material Substances 0.000 abstract description 3
- 239000003921 oil Substances 0.000 description 105
- 230000008859 change Effects 0.000 description 14
- 238000006073 displacement reaction Methods 0.000 description 13
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 description 12
- 238000000034 method Methods 0.000 description 8
- 238000010438 heat treatment Methods 0.000 description 6
- 229910052757 nitrogen Inorganic materials 0.000 description 6
- 230000008569 process Effects 0.000 description 6
- 230000006978 adaptation Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 4
- 230000009286 beneficial effect Effects 0.000 description 3
- 230000009467 reduction Effects 0.000 description 3
- 238000012986 modification Methods 0.000 description 2
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- 239000010729 system oil Substances 0.000 description 1
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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
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2278—Hydraulic circuits
- E02F9/2289—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 pilot operation subassembly, the hydraulic pump, the control subassembly of target pressure, target power control subassembly and controller, the pilot operation subassembly links to each other with the master control valves and is used for sending the action signal to the master control valves, move with control work end, the hydraulic pump supplies oil to the master control valves, the control subassembly of target pressure is used for carrying pump flow control signal to the hydraulic pump, the control subassembly of target power is used for carrying pump power control signal to the hydraulic pump, controller and pilot operation subassembly, control subassembly of target pressure and target power control subassembly link to each other, the controller is used for controlling the control subassembly of target pressure and the control subassembly of target power to start and close according to the action signal. The hydraulic control system can enable the actual flow demand of the breaking hammer to be adaptive to the flow provided by the oil source, thereby avoiding the waste of system energy consumption, the overheating of the system, the insufficient hammering force and frequency, and further improving the construction efficiency, reliability and stability of the system.
Description
Technical Field
The application relates to the technical field of hydraulic control, in particular to a hydraulic control system.
Background
Engineering machinery main machines, such as excavators, are often equipped with hydraulic breaking hammers for breaking construction.
At present, a hydraulic control system for driving a breaking hammer on a main machine usually adopts a control mode of only taking power control as a target for the output flow of a hydraulic pump, and limits the pressure of a breaking oil inlet line through an overflow valve in a loop, wherein the output P/Q curve of the hydraulic pump in the system is shown as a curve a in figure 1. For the system, when the output power of the system is larger, the output flow is possible to be more, according to the load characteristic of the breaking hammer, the more the oil inlet flow of the hammer is, the higher the oil inlet pressure of the hammer is, the oil inlet pressure is changed in a circulating fluctuation mode, the breaking and striking performance is better when the oil inlet pressure is large, but the rated pressure requirement of the hammer and the system cannot be exceeded, otherwise, the production damage is possible, therefore, if the oil source power is set to be too large, the oil inlet pressure of a loop is too large, an overflow valve is opened to overflow, the heating temperature of the system is too high, the energy consumption is wasted, and if the oil source power is set to be too small, the oil inlet flow is insufficient, the oil inlet working pressure is insufficient, and the working frequency and the striking force of the hammer are insufficient. In order to prevent the system from overflowing during the operation of the breaking hammer, the system output pressure P and the system output flow Q can only be controlled within the range of the area a shown in fig. 1. For a piston reciprocating hydraulic breaking hammer, a relation curve of hammer oil inlet pressure and time is shown in fig. 2, a working cycle of the piston reciprocating hydraulic breaking hammer is divided into two stages of a piston stroke and a 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 reduction amount of a hammer oil inlet path during the stroke, the hammer oil inlet flow during the stroke needs a large flow rate, 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 oil return resistance and nitrogen pressure, the hammer oil inlet pressure can be increased to the maximum value along with the piston 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 on the oil source in the later stage of the piston return stroke is smaller than the requirements in the earlier stage of the stroke and the return stroke, namely the actual power requirement of the breaking hammer in the working cycle is changed, and the load pressure needed in the later stage of the return stroke is smaller. When the hammer is used, when parameters such as the frequency and the nitrogen pressure of the hammer are adjusted or the hammer is replaced by a breaking hammer of different types, the actual power requirement of the hammer on the system can be changed. In the working process, as the oil temperature of the hydraulic system rises, the leakage rate of the hydraulic loop and the hammer can be increased, and if the oil source power is not correspondingly increased to improve the supply flow rate of the system, the striking force and the frequency of the hammer can be reduced, so that the construction is influenced. Furthermore, there are other actuators in the host system in addition to the demolition hammer, and the hammer and other actuators typically have different power requirements on the system, and engine speed variations can also affect the magnitude of the output power of the pump.
According to the above situation, the impact of various factors on the breaking hammer and the host control system, the hammer changes the power, flow and oil supply pressure requirements of the hydraulic system, and the overall performance of the system needs to be considered, while the host control system in the prior art often only adopts a mode of power target control and overflow pressure limiting, 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 hammering force and frequency are insufficient, thereby the construction efficiency, the reliability and the working stability of the machine are affected, the host adapts to the breaking hammers with different parameters poorly, and the system matching is difficult.
Therefore, how to avoid the problem that the actual flow demand of the hammer cannot be adapted to the flow provided by the oil source due to the combination of the overflow pressure limiting mode and the target control by only adopting power is a technical problem to be solved by the technical personnel in the field.
Disclosure of Invention
The application aims at providing a hydraulic control system, can adjust system work end oil feed flow to realize flow adaptive 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 is used for controlling the action of the working end;
the pilot operation assembly is connected with the main control valve group and 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 bank and used for supplying oil to the main control valve bank;
the target pressure control assembly is connected with the hydraulic pump and is used for transmitting a pump flow adjusting signal to the hydraulic pump so that the hydraulic pump can adjust the output flow according to the pump flow adjusting signal;
the target power control assembly is connected with the hydraulic pump and used for transmitting a pump power adjusting signal to the hydraulic pump so that the hydraulic pump adjusts the 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 value of the target pressure control assembly and the target power control assembly.
In some embodiments, the target pressure control assembly includes a pilot element, a pressure sensing element, a target pressure setting element, and a first throttling element, a control end of the pilot element is connected to the controller, an inlet of the pilot element is connected to an outlet of the hydraulic pump, an outlet of the pilot element is connected to one end of the first throttling element, one of control ends of the pressure sensing element, and an 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 an inlet of the target pressure setting element, respectively, an outlet of the pressure sensing element is connected to the signal output oil path of the target pressure control assembly, and an 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 defining element connected to the signal output oil passage of the target pressure control assembly and to the oil tank.
In some embodiments, the second throttling element is arranged on an oil path connecting the outlet of the pressure sensing element and the signal output oil path of the target pressure control assembly, and the oil path connecting the outlet of the target pressure setting element and the signal output oil path of the target pressure control assembly.
In some embodiments, the device further comprises a parameter regulator, the parameter regulator is connected with a 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 regulator via 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 regulated through the parameter regulator via the controller.
In some embodiments, the pressure sensing element is a two-position, three-way proportional valve.
In some embodiments, the actuation element is a two-position, two-way solenoid valve.
In some embodiments, the system further comprises an overflow valve group, wherein the overflow valve group is connected with an outlet of the hydraulic pump.
In some embodiments, the controller is connected with the control end of the overflow valve group, and the rated pressure of the overflow valve group is set through the controller by the parameter regulator.
In some embodiments, the system further comprises a signal receiving and adjusting component, the signal receiving and adjusting component is configured to receive the pump flow adjusting signal and the pump power adjusting signal and adjust the output flow and the output power of the hydraulic pump according to the pump flow adjusting signal and the pump power adjusting signal, respectively, and the signal receiving and adjusting component comprises:
the first regulator is connected with a signal output oil circuit of the target pressure control assembly and the hydraulic pump and 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 the pump power regulating signal so as to regulate the output power of the hydraulic pump.
Compared with the background art, the hydraulic control system provided in the embodiment of the present application includes a working end, a main control valve group, 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 group is connected to the working end, the main control valve group is used for controlling the action of the working end, the pilot operation assembly is connected to the main control valve group, the pilot operation assembly is used for sending an action signal to the main control valve group to control the action of the working end, the hydraulic pump is connected to the main control valve group, the hydraulic pump is used for supplying oil to the main control valve group, the target pressure control assembly is connected to the hydraulic pump, the target pressure control assembly is used for sending a pump flow regulation signal to the hydraulic pump to enable the hydraulic pump to regulate an output flow according to the pump flow regulation signal, the target power control assembly is connected to the hydraulic pump, and the target power control assembly is used for sending a pump power regulation signal to the hydraulic pump, the controller is used for receiving the action signal of the pilot operation assembly, controlling the target pressure control assembly and the target power control assembly to be started and closed according to the action signal and setting the target value of the control target pressure control assembly and the target power control assembly.
Specifically, the working end may be a breaking hammer, and in the construction of the breaking hammer, when the pilot operation assembly is operated, the breaking hammer starts to operate, and the controller knows the hammer operation through the pilot operation assembly, and then opens the target pressure control function of the target pressure control assembly, so that the maximum oil inlet load pressure of the breaking hammer is controlled by the target pressure control assembly, that is: 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 adjusting signal to enable the displacement of the hydraulic pump to be rapidly reduced 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 adjusting signal is reduced to the minimum, the discharge capacity of the hydraulic pump is recovered 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, the output flow of the hydraulic pump is irrelevant to the pressure on the oil inlet path of the breaking hammer, the output flow of the hydraulic pump depends on power setting, and as long as the load power does not exceed the maximum power which can be provided by the hydraulic pump when the hammer acts, the controller can set the power of the hydraulic pump to be as high as possible through the target power control assembly, so that the system can provide the flow to the oil inlet of the breaking hammer as much as possible, and overflow loss and system heating problems can not be generated when the power is set to be too large.
The hydraulic control system that this application embodiment provided has target pressure control assembly, and target pressure control assembly realizes advancing oil circuit target pressure control to the quartering hammer through the discharge capacity mode of control hydraulic pump, so, target pressure control assembly and target power control assembly in the system can adjust the oil feed flow of quartering hammer together to realize flow adaptive control. Compared with the traditional method of controlling the output flow of the hydraulic pump by adopting power as a target control and an overflow pressure limiting mode, the hydraulic control system provided by the embodiment of the application can bring the following beneficial effects:
firstly, the problems of overheating of a system and waste of oil consumption caused by overhigh power adjustment of a hydraulic pump when a hydraulic control system is matched with a breaking hammer are solved;
the adaptability problem 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 operation performance of the breaking hammer is improved;
thirdly, the problem that the frequency of the striking force of the breaking hammer is changed due to the change 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;
fourthly, the problems of system overflow loss and heating caused by the change of flow demand or system output caused by the frequency adjustment of the breaking hammer, the change of nitrogen pressure parameters and the change of the rotating speed of an engine in the use process of the breaking hammer are solved;
fifthly, the problem of adaptation of the same host to breaking hammers with different parameter specifications is solved, the problem of system overflow or poor breaking and hitting performance which is possibly caused by mismatching of power and pressure when a user replaces different breaking hammers is solved, the operation setting is simplified, the requirements of power and pressure adjustment between the breaking hammers and other actuators are met, and the overall performance of the system is improved.
To sum up, the hydraulic control system that this application embodiment provided can make the actual flow demand of quartering hammer suit with the flow that the oil source provided (or the output flow of hydraulic pump) to avoid the extravagant, the system of system energy consumption overheated, hammer hitting power and frequency not enough, and then improve system efficiency of construction, reliability and stability, and the host computer is better to the quartering hammer adaptation of different parameters, and the system matches also more easily simultaneously.
Drawings
In order to more clearly illustrate the embodiments of the present application or the technical solutions in the prior art, the drawings needed to be used in the description of the embodiments or the prior art will be briefly introduced below, it is obvious that the drawings in the following description are only embodiments of the present application, and for those skilled in the art, other drawings can be obtained according to the provided drawings without creative efforts.
FIG. 1 is a graph illustrating a load pressure versus output flow of a hydraulic pump of a prior art hydraulic control system;
FIG. 2 is a graph illustrating the relationship between the inlet pressure of a breaking hammer and the time of a hydraulic control system in 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 illustrating the load pressure of a hydraulic pump versus output flow for the hydraulic control system of the present embodiment;
fig. 5 is a graph illustrating a relationship between a breaking hammer oil inlet pressure and time of the hydraulic control system in the embodiment of the present application.
Wherein:
1-a hydraulic pump, 2-a target pressure control assembly, 3-a main control valve bank, 4-a working end, 5-a controller, 6-a pilot operation assembly, 7-a target power control assembly, 8-an overflow valve bank, 9-a parameter regulator and 10-an actuator;
21-make element, 22-pressure sensing element, 23-pressure defining element, 24-target pressure setting element, 25-first throttling element, 26-second throttling element.
Detailed Description
The technical solutions in the embodiments of the present application will be described clearly and completely with reference to the drawings in the embodiments of the present application, and it is obvious that the described embodiments are only some embodiments of the present application, and not all embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present application.
In order to enable those skilled in the art to better understand the scheme of the present application, the present application will be described in further detail with reference to the accompanying drawings and the detailed description.
Referring to fig. 3, 4 and 5, fig. 3 is a schematic diagram of a hydraulic control system in an embodiment of the present application; FIG. 4 is a schematic diagram illustrating a load pressure versus an output flow of a hydraulic pump of the hydraulic control system according to an embodiment of the present application; fig. 5 is a schematic diagram of a relation curve between an oil inlet pressure of a breaking hammer and time of a hydraulic control system in 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 main 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 main control valve group 3 is connected to the working end 4, the main control valve group 3 is used to control the operation of the working end 4, the pilot operation assembly 6 is connected to the main control valve group 3, the pilot operation assembly 6 is used to send an operation signal to the main control valve group 3 to control the operation of the working end 4, the hydraulic pump 1 is connected to the main control valve group 3, the hydraulic pump 1 is a system oil source, the hydraulic pump 1 is used to supply oil to the main 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 send a pump flow adjustment signal to the hydraulic pump 1, so that the hydraulic pump 1 adjusts an output flow according to the pump flow adjustment signal, the target power control assembly 7 is connected to the hydraulic pump 1, the target power control assembly 7 is used for transmitting a pump power adjusting signal to the hydraulic pump 1 to enable the hydraulic pump 1 to adjust the output power according to the pump power adjusting signal, the controller 5 is connected with the pilot operation assembly 6, the target pressure control assembly 2 and the target power control assembly 7, and the controller 5 is used for receiving an action signal of the pilot operation assembly 6, controlling the target pressure control assembly 2 and the target power control assembly 7 to be started and closed according to the action signal and setting the target value of the target pressure control assembly 2 and the target power control assembly 7.
Specifically, the working end 4 may be a breaking hammer, and during 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 operate, and the controller 5 starts the target pressure control function of the target pressure control assembly 2 after knowing the hammer operation 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, that is: 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 adjusting signal to enable the displacement of the hydraulic pump 1 to be rapidly reduced 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 adjusting 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 does not exceed the maximum power which can be provided by the hydraulic pump 1 during the action of the hammer, 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 the flow to the oil inlet of the breaking hammer as much as possible, and overflow loss and the problem of system heating cannot be caused by overlarge power setting.
In addition, the hydraulic control system also comprises other actuators 10, the actuators 10 are connected with a master valve group 3, and the master valve group 3 is used for controlling the actions of the breaking hammer or other actuators 10.
The hydraulic control system that this application embodiment provided has target pressure control assembly 2, and target pressure control assembly 2 realizes advancing oil circuit target pressure control to the quartering hammer through the discharge capacity mode of control hydraulic pump 1, so, target pressure control assembly 2 in the system can adjust the oil feed flow of quartering hammer together with target power control assembly 7 to realize flow adaptive control. Compared with the traditional method of controlling the output flow of the hydraulic pump 1 by adopting power as a target control and an overflow pressure limiting mode, the hydraulic control system provided by the embodiment of the application can bring the following beneficial effects:
firstly, the problems of overheating of a system and waste of oil consumption caused by overhigh power adjustment of a hydraulic pump 1 when a hydraulic control system is matched with a breaking hammer are solved;
secondly, the problem of adaptability of a 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 operation performance of the breaking hammer is improved;
thirdly, the problem that the frequency of the striking force of the breaking hammer is changed due to the change 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;
fourthly, the problems of system overflow loss and heating caused by the change of flow demand or system output caused by the frequency adjustment of the breaking hammer, the change of nitrogen pressure parameters and the change of the rotating speed of an engine in the use process of the breaking hammer are solved;
fifthly, the problem of adaptation of the same host to breaking hammers with different parameter specifications is solved, the problem of system overflow or poor breaking and hitting performance which is possibly caused by mismatching of power and pressure when a user replaces different breaking hammers is solved, the operation setting is simplified, the requirements of power and pressure adjustment between the breaking hammers and other actuators 10 are met, and the overall performance of the system is improved.
To sum up, the hydraulic control system that this application embodiment provided can make the actual flow demand of quartering hammer suit with the flow that the oil source provided (or the output flow of hydraulic pump 1) to avoid the extravagant, the overheated, hammer hitting power of system energy consumption and frequency not enough, and then improve system efficiency of construction, reliability and stability, and the host computer is better to the quartering hammer adaptation of different parameters, and the system matches also more easily simultaneously.
In some embodiments, the hydraulic control system further comprises a signal receiving and adjusting component for receiving the pump flow adjusting signal and the pump power adjusting signal and adjusting the output flow and the output power of the hydraulic pump 1 according to the pump flow adjusting signal and the pump power adjusting signal, respectively. Specifically, the signal receiving and adjusting assembly comprises a first adjuster and a second adjuster, wherein the first adjuster is connected with the signal output oil path 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 receives the pump flow rate adjustment signal from the target pressure control module 2, and the stronger the adjustment signal, the smaller the displacement of the hydraulic pump 1 is adjusted, and the second regulator of the hydraulic pump 1 receives the pump power adjustment signal from the pump target power control module 7 and controls the pump displacement together to adjust the pump power.
It should be noted that the signal receiving and adjusting module of the hydraulic pump 1 converts the pump flow adjusting signal and the pump power adjusting signal, and determines the real-time displacement of the hydraulic pump 1 according to the smaller displacement control requirement after comparison.
In some embodiments, the target pressure control assembly 2 includes a pilot 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 valve element 21 is connected with the controller 5, the inlet of the valve element 21 is connected with the outlet of the hydraulic pump 1, and the outlet of the valve element 21 is connected with one end of the first throttling element 25, one of the control ends 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 connected with the other control end of the pressure sensing element 22 and the inlet of the target pressure setting element 24 respectively, the outlet of the pressure sensing element 22 is connected with the signal output oil path of the target pressure control assembly 2, and the outlet of the target pressure setting element 24 is connected with the signal output oil path of the target pressure control assembly 2 and the oil tank. The pilot element 21 receives control from the controller 5, the pilot element 21 is used to turn on or off the target pressure control function of the target pressure control unit 2 to the system, the target pressure setting element 24 receives a target pressure setting signal from the controller 5, and the signal of the target pressure control unit 2 outputs the output pressure of the oil passage as a pump flow rate adjustment signal.
Of course, according to actual requirements, the pressure sensing element 22 is a two-position three-way proportional valve, the actuation element 21 is a two-position two-way electromagnetic valve, and when the actuation element 21 is in the left position, the target pressure control function of the target pressure control assembly 2 is closed, and when the actuation 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 a signal output oil path and an oil tank of the target pressure control assembly 2, the pressure limiting element 23 is specifically a relief 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 is prevented from being influenced and the hydraulic pump 1 is prevented from being damaged due to the overlarge output signal.
In some embodiments, a second throttling element 26 is provided on an oil path connecting the outlet of the pressure sensing element 22 with the signal output oil path of the target pressure control assembly 2, and an oil path connecting the outlet of the target pressure setting element 24 with the signal output oil path of the target pressure control assembly 2.
In this way, the target pressure control assembly 2 can sense the pressure change on the oil inlet path of the breaking hammer, when it senses that the pressure on the oil inlet path exceeds the target pressure set by the target pressure control assembly 2, the target pressure setting element 24 will automatically open, and due to the throttling pressure difference effect of the first throttling element 25, the acting force on the two control ends of the pressure sensing element 22 will change, so as to change the internal valve opening of the pressure sensing element 22, and further increase the magnitude of the pump flow adjusting signal output by the signal output oil path of the target pressure control assembly 2, so as to cause the displacement of the hydraulic pump 1 to be rapidly reduced, until the breaking hammer oil pressure is reduced to be slightly higher than the target pressure, the opening of the pressure sensing element 22 of the target pressure control assembly 2 will be reduced, the pump flow adjusting signal will stop increasing, so as to cause the displacement of the hydraulic pump 1 to stop being adjusted to be small, when the breaking hammer oil pressure is close to or lower than the target pressure, the pressure setting element of the target pressure control assembly 2 is automatically closed, then the opening of the pressure sensing element 22 tends to be closed, the pump flow adjusting signal is reduced to the minimum, the displacement of the hydraulic pump 1 is recovered to the maximum, so that the pressure control on the oil inlet path of the breaking hammer is realized, namely, the target pressure control function of the hammer is realized, and as long as the pressure of the oil inlet path 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, namely, when the pump power adjusting signal and the maximum displacement of the hydraulic pump 1 are not considered, the output flow of the pump is provided according to the flow required by the breaking hammer.
It can be understood that, the signal loop of the target pressure control assembly 2 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 regulator on the pump adjusts the displacement of the pump according to the signal to control the breaking hammer oil inlet pressure. In addition, the target pressure control module 2 has a function of turning on or off the load pressure of the breaker inlet line by the controller 5 connected thereto, and the target pressure control module 2 also has a function of preventing an output pressure signal thereof from being excessive, thereby preventing control stability from being affected and the hydraulic pump 1 from being damaged due to the excessive signal.
The target pressure of the target pressure control assembly 2 can be set electronically or manually by the controller 5 or 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 through the controller 5 by the parameter regulator 9, the controller 5 is connected to a control end of the target power control assembly 7, and an output signal of the target power assembly 7 is regulated through the controller 5 by the parameter regulator 9.
In some embodiments, the hydraulic control system further comprises an overflow valve set 8, and the overflow valve set 8 is connected to an outlet of the hydraulic pump 1. Meanwhile, the controller 5 is connected with the control end of the overflow valve group 8, and the rated pressure of the overflow valve group 8 is set through the controller 5 by the parameter regulator 9. The overflow valve group 8 can limit the maximum outlet pressure of the hydraulic pump 1, and the overflow pressure has a multi-stage or proportional regulation function.
The controller 5 is configured to receive a hammer pilot control signal (an operation signal) from the pilot operation unit 6 and a parameter adjustment signal from the parameter adjuster 9, set a target pressure in the target pressure control unit 2 or shut off the adjustment of the hydraulic pump 1 by the target pressure control unit 2 based on the received signals, and is configured to adjust the setting by a pump output adjustment signal from the target output control unit 7 and set an overflow opening pressure value of the overflow valve group 8.
The following specifically explains the beneficial effects brought by the hydraulic control system provided by the embodiment of the application.
1. In the process of breaking hammer construction, when the pilot operation assembly 6 is operated, the breaking hammer starts to act, and the controller 5 knows the breaking hammer acts through the pilot operation assembly 6, the target pressure control function of the target pressure control assembly 2 is started, and the target pressure of the target pressure control assembly 2 is set to be lower than the set pressure of the overflow valve group 8 but not lower than the maximum load pressure required by the breaking hammer, so that the maximum breaking hammer inlet load pressure is controlled by the target pressure control assembly 2, namely when the breaking hammer inlet load pressure is higher than the target pressure of the target pressure control assembly 2, the target pressure control assembly 2 outputs a pump flow adjusting signal to rapidly reduce the displacement of the hydraulic pump 1, so that the maximum breaking hammer inlet pressure is controlled to be slightly higher than the target pressure of the target pressure control assembly 2 but to be lower than the set pressure of the overflow valve group 8, thereby avoiding the system overflow valve to open, the output flow of the hydraulic pump 1 then being dependent on the power setting when the breaking hammer inlet pressure is below the target pressure, and the controller 5 can set the pump power as high as possible via the target power control assembly 7 as long as the load power does not exceed the maximum power that the pump can provide when the hammer is acting.
As shown in fig. 4, when the breaking hammer is operated, the power setting of the hydraulic pump 1 can be set according to the P/Q curve c of the hydraulic pump 1, 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 flow rate range of the system supplied to the breaking hammer includes the range of the area a and the range of the area B, so that the system can supply as much flow rate as possible to the breaking hammer oil inlet, and the overflow loss and the system heating problems can not be generated even if the power setting is too large.
2. After the setting mode is adopted, when the hammer acts, the problem of system overflow cannot be caused, and the power of the pump can be set to be the maximum, so that the application range of the pump for flow supply of the hammer is improved, namely, in the working stage that the stroke and the 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 the hammer as much as possible in the maximum power range, so that the oil inlet pressure drop amount or fluctuation amount in the stage is reduced, when the return stroke of the hammer piston is close to a top dead center stage, the oil inlet pressure of the hammer reaches the maximum, when the oil inlet pressure of the hammer is higher than the target pressure of the target pressure control assembly 2, the output flow of the pump is automatically reduced, and the actually required flow of the hammer is also reduced, so that the output flow of the system is automatically adapted to the flow demands of different stages in the working cycle period of the hammer.
As shown in fig. 5, due to the increase of the oil inlet flow of the breaking hammer, the oil inlet pressure of the breaking hammer is increased to curve g during the hammer action, and meanwhile, due to the reduction of the oil inlet pressure of the breaking hammer and the reduction of the pressure fluctuation range, the hitting performance of the breaking hammer is certainly improved.
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, the flow leakage loss in a loop is increased due to the fact that the oil temperature rises, the hammer automatically increases the absorption power, the output flow of the hydraulic pump 1 is increased, and therefore the oil inlet flow leakage loss and the oil inlet pressure drop of the breaking hammer 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 quartering hammer use, need adjust the quartering hammer frequency through the frequency modulation valve sometimes, frequency modulation then hammer oil feed pressure then can rise, quartering hammer oil feed demand flow then reduces, in addition because the temperature influence leads to nitrogen pressure to rise, thereby lead to the rise of oil feed pressure, because the restriction of target pressure control assembly 2 to the highest operating pressure of quartering hammer oil feed and the self-adaptation adjustment function of system to the flow, consequently, can avoid the regulation of frequency or nitrogen pressure change to lead to pressure to surpass overflow valve cracking pressure, thereby produce overflow loss.
5. For the breaking hammer with different requirements on pressure and flow parameters, when the breaking hammer is matched with the same host, the requirement on the maximum oil inlet pressure of the breaking hammer can meet the requirement on the type of the breaking hammer only by simply utilizing the parameter regulator 9 to set the target pressure of the target pressure control assembly 2 through the controller 5, the system power can be uniformly set to be maximum, the problem of system overflow cannot occur, the application range of the host to the hammer is enlarged, and the application operation is simplified.
In addition, when the existing breaking hammer and other actuators 10 in the system are operated, when the breaking hammer is operated to act, the controller 5 senses the action of the breaking hammer through the pilot operation assembly 6, opens a target pressure control group to perform a target pressure control function on the inlet oil of the breaking hammer, and sets the overflow opening pressure of the overflow valve group 8 to be higher than the target pressure set by the target pressure control assembly 2, at the moment, the working pressure of the inlet oil of the breaking hammer 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 control function of the target pressure control assembly 2 on the target pressure of the system is closed through the controller 5, the maximum working pressure of the pump opening 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 the requirements of the breaking hammer on power and pressure different from those of other actuators 10.
It is noted that, in this specification, relational terms such as first and second, and the like 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. The principle and the implementation of the present application are explained herein by using specific examples, and the above descriptions of the examples are only used to help understand the scheme and the core idea of the present application. It should be noted that, for those skilled in the art, it is possible to make several improvements and modifications to the present application without departing from the principle of the present application, and such improvements and modifications also fall within the scope of the claims of the present application.
Claims (10)
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 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 bank and used for supplying oil to the main control valve bank;
the target pressure control assembly is connected with the hydraulic pump and is used for transmitting a pump flow adjusting signal to the hydraulic pump so that the hydraulic pump can adjust the output flow according to the pump flow adjusting signal;
the target power control assembly is connected with the hydraulic pump and used for transmitting a pump power adjusting signal to the hydraulic pump so that the hydraulic pump can adjust the 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 value of the target pressure control assembly and the target power control assembly.
2. The hydraulic control system of claim 1, wherein the target pressure control assembly includes a pilot element, a pressure sensing element, a target pressure setting element, and a first throttling element, the control end of the burning element is connected with the controller, the inlet of the burning element is connected with the outlet of the hydraulic pump, the outlet of the pilot element is connected with 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 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 an 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.
3. The hydraulic control system of claim 2, wherein the target pressure control assembly further includes a pressure defining element connected to the signal output oil path of the target pressure control assembly and the tank.
4. The hydraulic control system according to claim 2, wherein a second throttling element is provided on an oil passage through which the outlet of the pressure sensing element is connected to the signal output oil passage of the target pressure control assembly, and an oil passage through which the outlet of the target pressure setting element is connected to the signal output oil passage of the target pressure control assembly.
5. The hydraulic control system of claim 2, further comprising a parameter regulator, the parameter regulator being connected to the controller, the controller being connected to a control terminal of the target pressure setting element, the target pressure setting element being set by the parameter regulator via the controller, the controller being connected to a control terminal of the target power control assembly, the output signal of the target power assembly being regulated by the parameter regulator via the controller.
6. A hydraulic control system as claimed in claim 2, wherein said pressure sensing element is a two-position, three-way proportional valve.
7. The hydraulic control system of claim 2, wherein the actuation member is a two-position, two-way solenoid valve.
8. The hydraulic control system of claim 5, further comprising an overflow valve block connected to an outlet of the hydraulic pump.
9. A hydraulic control system as set forth in claim 8 wherein said control is connected to a control end of said spill valve block and a set pressure of said spill valve block is set by said parameter adjuster via said control.
10. The hydraulic control system according to any one of claims 1-9, further comprising a signal receiving and adjusting assembly for receiving the pump flow adjusting signal and the pump power adjusting signal and adjusting the output flow and the output power of the hydraulic pump according to the pump flow adjusting signal and the pump power adjusting signal, respectively, the signal receiving and adjusting assembly comprising:
the first regulator is connected with a signal output oil path of the target pressure control assembly and the hydraulic pump and used for receiving the 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 component and the hydraulic pump and is used for receiving the pump power regulating signal so as to regulate the output power of the hydraulic pump.
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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 |
| 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 |
-
2022
- 2022-07-26 CN CN202210885238.1A patent/CN115110596B/en active Active
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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