CN113883109A - Engineering machinery control device and engineering machinery - Google Patents
Engineering machinery control device and engineering machinery Download PDFInfo
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- CN113883109A CN113883109A CN202111105865.0A CN202111105865A CN113883109A CN 113883109 A CN113883109 A CN 113883109A CN 202111105865 A CN202111105865 A CN 202111105865A CN 113883109 A CN113883109 A CN 113883109A
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- 230000007246 mechanism Effects 0.000 claims abstract description 9
- 230000001502 supplementing effect Effects 0.000 claims description 18
- 238000010276 construction Methods 0.000 claims description 13
- 230000008859 change Effects 0.000 claims description 5
- 239000003921 oil Substances 0.000 abstract description 194
- 239000010720 hydraulic oil Substances 0.000 abstract description 15
- 230000009471 action Effects 0.000 abstract description 5
- 238000001914 filtration Methods 0.000 abstract description 3
- 238000005553 drilling Methods 0.000 description 9
- 238000000034 method Methods 0.000 description 5
- 230000008569 process Effects 0.000 description 5
- 239000002689 soil Substances 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 238000001595 flow curve Methods 0.000 description 3
- 230000004075 alteration Effects 0.000 description 1
- 238000001514 detection method Methods 0.000 description 1
- 230000007935 neutral effect Effects 0.000 description 1
- 230000002787 reinforcement Effects 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
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Classifications
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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
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
- F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
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- E—FIXED CONSTRUCTIONS
- E21—EARTH OR ROCK DRILLING; MINING
- E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
- E21B7/00—Special methods or apparatus for drilling
- E21B7/02—Drilling rigs characterised by means for land transport with their own drive, e.g. skid mounting or wheel mounting
- E21B7/021—With a rotary table, i.e. a fixed rotary drive for a relatively advancing tool
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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
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
- F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
- F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/0401—Valve members; Fluid interconnections therefor
- F15B2013/0412—Valve members; Fluid interconnections therefor with three positions
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/405—Flow control characterised by the type of flow control means or valve
- F15B2211/40507—Flow control characterised by the type of flow control means or valve with constant throttles or orifices
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/565—Control of a downstream pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/615—Filtering means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
- F15B2211/7058—Rotary output members
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/80—Other types of control related to particular problems or conditions
- F15B2211/85—Control during special operating conditions
- F15B2211/851—Control during special operating conditions during starting
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/80—Other types of control related to particular problems or conditions
- F15B2211/86—Control during or prevention of abnormal conditions
- F15B2211/8613—Control during or prevention of abnormal conditions the abnormal condition being oscillations
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- Life Sciences & Earth Sciences (AREA)
- Geology (AREA)
- Mining & Mineral Resources (AREA)
- Environmental & Geological Engineering (AREA)
- General Life Sciences & Earth Sciences (AREA)
- Geochemistry & Mineralogy (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention provides an engineering machinery control device and engineering machinery, which comprise a hydraulic pump, a reversing valve, an actuating mechanism, a first oil path and a second oil path, wherein the reversing valve comprises an oil inlet, a first working port, a second working port and an oil return port, the first oil path is provided with a first balance valve, the second oil path is provided with a second balance valve, a pilot port of the second balance valve is communicated with the first working port through a third oil path, the pilot port of the first balance valve is communicated with the second working port through a fourth oil path, the third oil path is provided with a first throttle valve, and the fourth oil path is provided with a second throttle valve. In the engineering machinery control device and the engineering machinery provided by the embodiment of the invention, the throttle valve is arranged, so that the pressure of the hydraulic oil after the hydraulic oil comes out of the reversing valve firstly passes through the filtering action of the throttle valve and then acts on the pilot port of the balance valve, the balance valve can be opened stably, and the stability of rotation starting is effectively improved.
Description
Technical Field
The invention relates to the technical field of engineering machinery, in particular to an engineering machinery control device and engineering machinery.
Background
The rotary drilling rig is a construction machine suitable for hole-forming operation in building foundation engineering, is mainly suitable for soil layer construction of sandy soil, cohesive soil, silty soil and the like, is widely applied to foundation construction of various foundations such as cast-in-place piles, continuous walls, foundation reinforcement and the like, generally adopts a hydraulic crawler type telescopic chassis, a self-lifting foldable drilling mast, a telescopic drill rod, vertical automatic detection and adjustment, hole depth digital display and the like, generally adopts hydraulic pilot control and load sensing for complete machine operation, and has the characteristics of light and comfortable operation and the like.
The rotary drilling rig has heavier boarding quality, the pressure impact is too high at the moment of starting and stopping, and then the pressure impact is sharply reduced, so that the rotary drilling rig has a stopping feeling at the moment of operation and a fluctuating feeling during the rotation. As shown in fig. 1, a control device for a rotary drilling rig includes a hydraulic pump 81, a directional control valve 82, a motor 83, a first oil path and a second oil path, wherein the directional control valve 82 is connected to the hydraulic pump 81, the first oil path is connected between the directional control valve 82 and the motor 83, and the second oil path is connected between the directional control valve 82 and the motor 83. The first oil path is provided with a first check valve 84 and a first balance valve 85 which are connected in parallel, the second oil path is provided with a second check valve 86 and a second balance valve 87 which are connected in parallel, and pilot oil ports of the first balance valve 85 and the second balance valve 87 are connected to an oil outlet of the reversing valve 82. A shuttle valve 88 is connected between the inlet of first check valve 84 and the inlet of second check valve 86. The control device of the rotary drilling rig further comprises a first oil supplementing valve 89, a second oil supplementing valve 90, a first overflow valve 92 and a second overflow valve 93, the first oil supplementing valve 89 and the second oil supplementing valve 90 are arranged between two ends of the motor 83, the first oil supplementing valve 89 and the second oil supplementing valve 90 are connected in series, the first overflow valve 92 and the second overflow valve 93 are also arranged between the brightness of the motor 83, and the first overflow valve 92 and the second overflow valve 93 are connected in parallel. Shuttle valve 88 is connected to the pilot oil ports of first and second spill valves 92 and 93, and the set pressures of first and second spill valves 92 and 93 are both 250 bar. In the rotary drilling rig control device, after hydraulic oil passes through the reversing valve 82, pressure directly acts on a pilot end of the first balance valve 85 or the second balance valve 87, so that the first balance valve 85 or the second balance valve 87 is easily influenced by load pressure fluctuation, the return oil flow of a motor is unstable, the rotating speed of the motor is uneven, and the rotation process is not stable; after the hydraulic oil reaches the motor 83, the oil returns through the opened first balance valve 85 or the opened second balance valve 87, and the existence of the oil return back pressure can cause instability when the first balance valve 85 or the second balance valve 87 is closed, so that the oil return flow rate is fluctuated; after the hydraulic oil passes through the reversing valve 82, the shuttle valve 88 acts on the pilot ends of the first overflow valve 92 and the second overflow valve 93 to control the opening of the valve core of the overflow valves, that is, the pressure fluctuation of the hydraulic oil after the reversing valve 82 can cause the change of the opening of the valve core of the overflow valves, thereby affecting the input flow fluctuation of the motor, namely, the opening and closing of the valve core of the overflow valves are affected by the pressure fluctuation of the load, causing the unstable input flow of the motor, resulting in the uneven rotating speed of the motor and the unstable rotation process.
Disclosure of Invention
The invention aims to provide an engineering machinery control device and engineering machinery, which reduce pressure impact at the moment of starting and stopping and have stable rotation.
The invention provides a drill rod of an engineering machinery control device, which comprises a hydraulic pump, a reversing valve, an actuating mechanism, a first oil way and a second oil way, the reversing valve comprises an oil inlet, a first working port, a second working port and an oil return port, the hydraulic pump is connected with the oil inlet of the reversing valve, the first oil path is connected between a first working port and the actuating mechanism, the second oil path is connected between a second working port and the actuating mechanism, a first balance valve is arranged on the first oil way, a second balance valve is arranged on the second oil way, a pilot port of the second balance valve is communicated with the first working port through the third oil way, the pilot port of the first balance valve is communicated with the second work through a fourth oil path, a first throttling valve is arranged on the third oil path, and a second throttling valve is arranged on the fourth oil path.
In one embodiment, the direction valve includes a valve core, a groove is formed in the valve core to form a channel communicating the oil inlet with the first working port or the second working port in the direction valve, an opening communicated with the groove is further formed in the valve core, the opening can be communicated with the first working port or the second working port, the opening includes a first portion and a second portion, the first portion is connected between the groove and the second portion, and the depth of the first portion is greater than that of the second portion.
In one embodiment, the second portion includes a semicircular arc portion and a square portion, the square portion is located between the semicircular arc portion and the first portion, and the first portion is arc-shaped.
In one embodiment, the actuator includes a first port and a second port, the first oil path is connected to the first port, and the second oil path is connected to the second port; an oil inlet and an oil outlet of the first balance valve are respectively communicated with the first working port and the first port, and an oil inlet and an oil outlet of the second balance valve are respectively communicated with the second working port and the second port; the first balance valve and the second balance valve are both composed of an overflow valve and a check valve which are connected in parallel.
In one embodiment, the engineering machinery control device further comprises an oil tank, and the oil inlet and the oil return port of the reversing valve are respectively connected to the oil tank; the oil tank is connected to the third oil passage at a position between the first throttle valve and the second counter balance valve, and the oil tank is also connected to the fourth oil passage at a position between the second throttle valve and the first counter balance valve.
In one embodiment, a third throttle valve is arranged between the oil tank and the third oil path, and a fourth throttle valve is arranged between the oil tank and the fourth oil path.
In one embodiment, the engineering machine control device further includes a first overflow valve and a second overflow valve, both of which are connected between the first oil path and the second oil path and connected in parallel with the actuator, a control end of the first overflow valve is connected to the second oil path, and a control end of the second overflow valve is connected to the first oil path.
In one embodiment, the set pressure of the first overflow valve and the second overflow valve is 120bar ± 20 bar.
In one embodiment, the engineering machinery control device further includes a third overflow valve, one end of the third overflow valve is connected to the oil tank, the other end of the third overflow valve is connected to an oil path between the hydraulic pump and the reversing valve, and a control end of the third overflow valve is connected to an oil path between the hydraulic pump and the reversing valve; or, the engineering machinery control device further comprises a first oil supplementing valve and a second oil supplementing valve, an oil inlet of the first oil supplementing valve is connected to the oil tank, an oil outlet of the first oil supplementing valve is connected to the first oil path, an oil inlet of the second oil supplementing valve is connected to the oil tank, and an oil outlet of the second oil supplementing valve is connected to the second oil path.
The invention also provides engineering machinery comprising the engineering machinery control device.
In the engineering machinery control device and the engineering machinery provided by the embodiment of the invention, the throttle valve is arranged, so that the pressure of the hydraulic oil after the hydraulic oil comes out of the reversing valve firstly passes through the filtering action of the throttle valve and then acts on the pilot port of the balance valve, the balance valve can be opened stably, and the stability of rotation starting is effectively improved.
Drawings
Fig. 1 is a schematic structural diagram of a control device for a construction machine.
Fig. 2 is a schematic structural diagram of a control device of a construction machine according to an embodiment of the present invention.
Fig. 3 is a schematic structural diagram of a valve core part of a reversing valve of the engineering machinery control device shown in fig. 2.
Fig. 4 is a graph comparing a stroke-flow curve of a directional control valve of the construction machine control device shown in fig. 2 with a conventional directional control valve.
Detailed Description
To further illustrate the technical means and effects of the present invention adopted to achieve the predetermined objects, the following detailed description of the embodiments, structures, features and effects of the present invention will be made with reference to the accompanying drawings and examples.
As shown in fig. 2, the construction machine control device according to the embodiment of the present invention includes a hydraulic pump 11, a selector valve 13, an actuator 15, a first oil passage 17, and a second oil passage 19. The direction change valve 13 includes an oil inlet port 130, a first working port 132, a second working port 134, and an oil return port 136, and the hydraulic pump 11 is connected to the oil inlet port 130 of the direction change valve 13 to supply oil to the system. The first oil passage 17 is connected between the first working port 132 and the actuator 15, and the second oil passage 19 is connected between the second working port 134 and the actuator 15. The first oil passage 17 is provided with a first balance valve 172, the second oil passage 19 is provided with a second balance valve 192, a pilot port of the second balance valve 192 is communicated with the first working port 132 through a third oil passage 21, a pilot port of the first balance valve 172 is communicated with the second working port 134 through a fourth oil passage 23, the third oil passage 21 is provided with a first throttle valve 212, and the fourth oil passage 23 is provided with a second throttle valve 232. Specifically, in this embodiment, the actuator 15 is a motor, more specifically, a rotary motor of a rotary drilling rig, but the actuator 15 may also be another actuator such as a hoisting motor.
In the engineering machinery control device provided by the embodiment of the invention, the throttle valve is arranged, so that the pressure of the hydraulic oil after the hydraulic oil comes out of the reversing valve firstly passes through the filtering action of the throttle valve and then acts on the pilot port of the balance valve, the balance valve can be opened more stably, and the stability of rotation starting is effectively improved.
In this embodiment, the reversing valve 13 may be an electromagnetic valve or a hydraulic control valve, and the reversing valve 13 is controlled to reverse by current or pilot pressure to control the action of the actuator, for example, to control the start, stop, and rotation direction of a rotary motor of the rotary drilling rig. Specifically, the reversing valve 13 may be a three-position four-way valve including a first position, a second position and a middle position, when the reversing valve 13 is in the first position (right position in the figure), the oil inlet 130 is communicated with the first working port 132, the oil return port 136 is communicated with the second working port 134, the first oil path 17 is a pressure oil path, the second oil path 19 is an oil return path, and the rotary motor rotates forward; when the reversing valve 13 is in the second position (left position in the figure), the oil inlet 130 is communicated with the second working port 134, the oil return port 136 is communicated with the first working port 132, the second oil path 19 is a pressure oil path, the first oil path 17 is an oil return path, and the rotary motor rotates reversely; when the reversing valve 13 is in the neutral position, the oil inlet 130, the first working port 132 and the second working port 134 are disconnected, and the rotary motor does not rotate.
Specifically, referring to fig. 3, the direction valve 13 includes a valve core 138, a groove 1382 is formed on the valve core 138 to form a channel communicating the oil inlet 130 with the first working port 132 or the second working port 134 in the direction valve 13, an opening 1384 communicated with the groove 1382 is further formed on the valve core 138, and the opening 1384 can be communicated with the first working port 132 or the second working port 134 in the moving process of the valve core 138. The opening 1384 includes a first portion 1386 and a second portion 1387, the first portion 1386 being connected between the recess 1382 and the second portion 1387, the first portion 1386 having a depth greater than a depth of the second portion 1387. By setting the opening 1384 to two portions having different depths, the slope of the curve of the micro-operation section of the selector valve 13 can be made lower, the output flow corresponding to the same pilot pressure can be made smaller, and the precision of the rotation alignment hole can be greatly improved. Specifically, the length of the opening 1384 is also greater than the prior art openings, thus reducing the dead band region of the diverter valve 13. More specifically, the second portion 1387 includes a semicircular arc portion and a square portion, the square portion is located between the semicircular arc portion and the first portion 1386, and the first portion 1386 is circular-arc-shaped. Referring to fig. 4, L1 is a stroke-flow curve of a valve element of the conventional direction valve, L2 is a stroke-flow curve of a valve element of the direction valve 13 of this embodiment, a dead zone interval (a dead zone interval refers to an area where the valve element moves a certain distance but no oil passes between the oil inlet 130 and the first working port 132 or the second working port 134, that is, the flow rate is 0) of the direction valve 13 of this embodiment is shorter than that of the prior art, and the slope of the curve of the micro-operation interval is reduced.
In this embodiment, the actuator 15 includes a first port 152 and a second port 154, the first oil path 17 is connected to the first port 152, the second oil path 19 is connected to the second port 154, when the first oil path 17 is a pressure oil path, the first port 152 is an oil inlet, and the second port 154 is an oil outlet; when the second oil passage 19 is a pressure oil passage, the second port 154 is an oil inlet, and the first port 152 is an oil outlet. Specifically, the oil inlet and the oil outlet of the first balance valve 172 are respectively communicated with the first working port 132 and the first port 152, and the oil inlet and the oil outlet of the second balance valve 192 are respectively communicated with the second working port 134 and the second port 154.
In this embodiment, the first balance valve 172 and the second balance valve 192 are both composed of a relief valve and a check valve connected in parallel, and the control end of the relief valve is the pilot port of the balance valve.
In this embodiment, the engineering machinery control device further includes an oil tank 25, and the oil inlet 130 and the oil return port 136 of the directional control valve 13 are respectively connected to the oil tank 25 to supply oil and return oil to the system.
In the present embodiment, the oil tank 25 is connected to the third oil passage 21 at a position between the first throttle valve 212 and the second balance valve 192, and the oil tank 25 is also connected to the fourth oil passage 23 at a position between the second throttle valve 232 and the first balance valve 172. Thus, when the reversing valve 13 is closed, the actuator 15 loses the oil supply of the hydraulic pump 11, and due to the effect of the oil return back pressure, part of the return oil can flow back to the oil tank 25 through the first throttle 212 or the second throttle 232, and the first throttle 212 or the second throttle 232 can stabilize the pressure of the pipeline from the second balance valve 192 to the reversing valve 13 or from the first balance valve 172 to the reversing valve 13, so that the second balance valve 192 or the first balance valve 172 is closed smoothly, and the smoothness of the slewing stop is effectively improved.
Further, a third throttle 27 is provided between the oil tank 25 and the third oil passage 21, and a fourth throttle 29 is provided between the oil tank 25 and the fourth oil passage 23. By arranging the third throttle valve 27 and the third throttle valve 29, the pressure in the section from the second balance valve 192 to the reversing valve 13 or from the first balance valve 172 to the reversing valve 13 can be better stabilized, so that the second balance valve 192 or the first balance valve 172 can be closed more smoothly, and the stability when the slewing is stopped is further improved.
In this embodiment, the control device for the construction machine further includes a first relief valve 30 and a second relief valve 31, both the first relief valve 30 and the second relief valve 31 are connected between the first oil passage 17 and the second oil passage 19 and are connected in parallel with the actuator 15, a control end of the first relief valve 30 is connected to the second oil passage 19, and a control end of the second relief valve 31 is connected to the first oil passage 17. The control ends of the first overflow valve 30 and the second overflow valve 31 are respectively connected to the second oil path 19 and the first oil path 17, so that the shuttle valve can be eliminated, the influence of load pressure fluctuation on the opening and closing of the overflow valves is avoided, the input flow in the working process of the executing mechanism is stabilized, the set pressures of the first overflow valve 30 and the second overflow valve 31 can be set to be lower, for example, the set pressures of the first overflow valve 30 and the second overflow valve 31 can be 120bar +/-20 bar, the set pressure is greatly reduced compared with the existing set pressure of 250bar, the system pressure is reduced, and the impact during rotation starting and stopping can be reduced.
In this embodiment, the control device for the engineering machine further includes a third overflow valve 32, one end of the third overflow valve 32 is connected to the oil tank 25, the other end of the third overflow valve 32 is connected to the oil path between the hydraulic pump 11 and the direction changing valve 13, and a control end of the third overflow valve 32 is connected to the oil path between the hydraulic pump 11 and the direction changing valve 13.
In this embodiment, the control device for the engineering machinery further includes a first oil replenishing valve 34 and a second oil replenishing valve 35, an oil inlet of the first oil replenishing valve 34 is connected to the oil tank 25, an oil outlet of the first oil replenishing valve 34 is connected to the first oil path 17, an oil inlet of the second oil replenishing valve 35 is connected to the oil tank 25, and an oil outlet of the second oil replenishing valve 35 is connected to the second oil path 19. Specifically, the first oil replenishment valve 34 and the second oil replenishment valve 35 are check valves to allow hydraulic oil to be replenished from the oil tank 25 to the first oil passage 17 or the second oil passage 19 to replenish the oil supplied to the high-pressure oil side of the actuator.
When the engineering machinery control device of the embodiment is started, hydraulic oil is delivered to the oil inlet 130 of the directional valve 13 through the hydraulic pump 11, the directional valve 13 is controlled to be steered, the oil inlet 130 is communicated with the first working port 132 or the second working port 134 (hereinafter, the communication between the oil inlet 130 and the first working port 132 is taken as an example), the hydraulic oil reaches the first oil path 17, the check valve of the first balance valve 172 is opened, the overflow valve of the first balance valve 172 is further opened, and the hydraulic oil reaches the first port 152 of the actuator 15 through the overflow valve of the first balance valve 172 through the first oil path 17 to drive the actuator 15 to move; after passing through the actuator 15, the oil flows out from the second port 154 to reach the second oil path 19, at this time, the high-pressure oil in the first oil path 17 reaches the pilot port of the second balance valve 192 through the third oil path 21 and the first throttle valve 212, the overflow valve of the second balance valve 192 is opened, the oil flows to the second working port 134 of the reversing valve 130 through the second oil path 19 and then reaches the oil return port 136 through the reversing valve 130, oil return is realized, and meanwhile, part of the oil return in the second oil path 19 passes through the second throttle valve 232 and the third throttle valve 27, and oil return is realized. In the process, the pressure of the hydraulic oil after coming out of the reversing valve 13 can be filtered by the first throttle valve 212 and then acts on the pilot port of the second balance valve 192 through the first throttle valve 212, so that the second balance valve 192 can be opened smoothly, and the stability of rotation starting is effectively improved.
When the engineering machinery control device of the embodiment is closed, the hydraulic pump 11 stops supplying oil to the actuating mechanism 15, due to the action of oil return back pressure, part of the oil returns after passing through the second throttling valve 232 and the third throttling valve 27, and the second throttling valve 232 and the third throttling valve 27 can stabilize the pressure of a section of pipeline from the second balance valve 192 to the reversing valve 13, so that the second balance valve 192 is closed stably, and the stability when the rotation is stopped is effectively improved.
The invention also provides engineering machinery comprising the engineering machinery control device.
Although the present invention has been described with reference to a preferred embodiment, it should be understood that various changes, substitutions and alterations can be made herein without departing from the spirit and scope of the invention as defined by the appended claims.
Claims (10)
1. An engineering machinery control device comprises a hydraulic pump (11), a reversing valve (13), an actuating mechanism (15), a first oil path (17) and a second oil path (19), wherein the reversing valve (13) comprises an oil inlet (130), a first working port (132), a second working port (134) and an oil return port (136), the hydraulic pump (11) is connected with the oil inlet (130) of the reversing valve (13), the first oil path (17) is connected between the first working port (132) and the actuating mechanism (15), the second oil path (19) is connected between the second working port (134) and the actuating mechanism (15), the engineering machinery control device is characterized in that a first balance valve (172) is arranged on the first oil path (17), a second balance valve (192) is arranged on the second oil path (19), a pilot port of the second balance valve (192) is communicated with the first working port (132) through a third oil path (21), the pilot port of the first balance valve (172) is communicated with the second working port (134) through a fourth oil path (23), a first throttle valve (212) is arranged on the third oil path (21), and a second throttle valve (232) is arranged on the fourth oil path (23).
2. The work machine control device according to claim 1, wherein the direction valve (13) includes a valve core (138), the valve core (138) is provided with a groove (1382) to form a passage communicating the oil inlet (130) with the first working port (132) or the second working port (134) in the direction valve (13), the valve core (138) is further provided with an opening (1384) communicating with the groove (1382), the opening (1384) can communicate with the first working port (132) or the second working port (134), the opening (1384) includes a first portion (1386) and a second portion (1387), the first portion (1386) is connected between the groove (1382) and the second portion (1387), and a depth of the first portion (1386) is greater than a depth of the second portion (1387).
3. The work machine control device according to claim 2, wherein the second portion (1387) includes a semicircular arc portion and a square portion, the square portion is located between the semicircular arc portion and the first portion (1386), and the first portion (1386) is circular arc-shaped.
4. The work machine control device according to claim 1, characterized in that the actuator (15) comprises a first port (152) and a second port (154), the first oil passage (17) being connected to the first port (152), the second oil passage (19) being connected to the second port (154); an oil inlet and an oil outlet of the first balance valve (172) are respectively communicated with the first working port (132) and the first port (152), and an oil inlet and an oil outlet of the second balance valve (192) are respectively communicated with the second working port (134) and the second port (154); the first balance valve (172) and the second balance valve (192) are both composed of a relief valve and a check valve which are connected in parallel.
5. The construction machine control device according to claim 1, further comprising an oil tank (25), wherein the oil inlet (130) and the oil return port (136) of the directional control valve (13) are respectively connected to the oil tank (25); the oil tank (25) is connected to a position between the first throttle valve (212) and the second counter balance valve (192) on the third oil passage (21), and the oil tank (25) is also connected to a position between the second throttle valve (232) and the first counter balance valve (172) on the fourth oil passage (23).
6. The construction machine control device according to claim 5, wherein a third throttle valve (27) is provided between the oil tank (25) and the third oil passage (21), and a fourth throttle valve (29) is provided between the oil tank (25) and the fourth oil passage (23).
7. The construction machine control device according to claim 1, further comprising a first relief valve (30) and a second relief valve (31), wherein the first relief valve (30) and the second relief valve (31) are both connected between the first oil passage (17) and the second oil passage (19) and are connected in parallel with the actuator (15), a control end of the first relief valve (30) is connected to the second oil passage (19), and a control end of the second relief valve (31) is connected to the first oil passage (17).
8. The control device for a construction machine according to claim 7, wherein the set pressure of the first relief valve (30) and the second relief valve (31) is 120bar ± 20 bar.
9. The construction machine control device according to claim 5, further comprising a third relief valve (32), one end of the third relief valve (32) being connected to the oil tank (25), the other end of the third relief valve (32) being connected to an oil path between the hydraulic pump (11) and the direction change valve (13), a control end of the third relief valve (32) being connected to an oil path between the hydraulic pump (11) and the direction change valve (13); or the engineering machinery control device further comprises a first oil supplementing valve (34) and a second oil supplementing valve (35), wherein an oil inlet of the first oil supplementing valve (34) is connected to the oil tank (25), an oil outlet of the first oil supplementing valve (34) is connected to the first oil path (17), an oil inlet of the second oil supplementing valve (35) is connected to the oil tank (25), and an oil outlet of the second oil supplementing valve (35) is connected to the second oil path (19).
10. A working machine comprising a working machine control device according to any of claims 1-9.
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| CN202111105865.0A CN113883109A (en) | 2021-09-22 | 2021-09-22 | Engineering machinery control device and engineering machinery |
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| CN202111105865.0A CN113883109A (en) | 2021-09-22 | 2021-09-22 | Engineering machinery control device and engineering machinery |
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Cited By (1)
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|---|---|---|---|---|
| CN115263843A (en) * | 2022-07-21 | 2022-11-01 | 燕山大学 | Rotary buffer valve for improving stability of rotary system and working method thereof |
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