CN116877519A - Hydraulic main valve and system of heavy-load mining excavator - Google Patents
Hydraulic main valve and system of heavy-load mining excavator Download PDFInfo
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- CN116877519A CN116877519A CN202310797975.0A CN202310797975A CN116877519A CN 116877519 A CN116877519 A CN 116877519A CN 202310797975 A CN202310797975 A CN 202310797975A CN 116877519 A CN116877519 A CN 116877519A
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- 238000005065 mining Methods 0.000 title claims abstract description 29
- 238000012216 screening Methods 0.000 claims abstract description 55
- 230000001502 supplementing effect Effects 0.000 claims description 22
- 238000001816 cooling Methods 0.000 claims description 10
- 230000000712 assembly Effects 0.000 claims description 4
- 238000000429 assembly Methods 0.000 claims description 4
- 239000003921 oil Substances 0.000 description 214
- 230000007246 mechanism Effects 0.000 description 16
- 230000009471 action Effects 0.000 description 8
- 150000001875 compounds Chemical class 0.000 description 5
- 230000001276 controlling effect Effects 0.000 description 4
- 230000000875 corresponding effect Effects 0.000 description 3
- 230000001105 regulatory effect Effects 0.000 description 3
- 230000008859 change Effects 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 230000035939 shock Effects 0.000 description 2
- 230000001174 ascending effect Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000006837 decompression Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000007935 neutral effect Effects 0.000 description 1
- 230000010349 pulsation Effects 0.000 description 1
- 230000035945 sensitivity Effects 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 239000010729 system oil Substances 0.000 description 1
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
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/08—Servomotor systems incorporating electrically operated control means
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- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Fluid-Pressure Circuits (AREA)
- Operation Control Of Excavators (AREA)
Abstract
The application discloses a hydraulic main valve and a system of a heavy-load mining excavator, wherein the main valve comprises a confluence joint and a plurality of working joints, the working joints comprise a plurality of first execution joints, a plurality of second execution joints, a first pilot oil path oil port, a second pilot oil path oil port, an annular oil duct and an oil return port, the confluence joint comprises a first signal screening valve and a plurality of main valve oil inlets, the main valve oil inlets are connected with the annular oil duct, and all the execution joints are connected in parallel through the annular oil duct.
Description
Technical Field
The application relates to a hydraulic main valve and a hydraulic main valve system of a heavy-duty mining excavator, and belongs to the technical field of engineering machinery.
Background
The 100-200 ton heavy-duty mining excavator is mainly used for heavy-duty large-scale construction sites such as metal mines and the like and bears the mining task of metal ore materials. Because of the characteristics of high pressure, large flow, complex working environment, severe working condition and the like, the hydraulic system of the heavy-load mining excavator has higher requirements on the operability and reliability. The main valve is used as the core part of the hydraulic excavator and is the key element for power transmission, and the performance of the whole excavator is directly determined. The hydraulic system of the 100-200 ton heavy-duty mine hydraulic excavator generally adopts an electric control positive flow system, and the main valve adopts an electric control positive flow main valve. The hydraulic system adopts a multi-pump and multi-loop main valve form, such as a three-pump and three-loop main valve form and a three-pump and four-loop main valve form. One or more single-loop throttling type hydraulic valves are added on the basis of a double-pump double-loop throttling type main valve of a large excavator below 100 tons to meet the system flow requirement. However, such systems require the preferential distribution of flow between the actuators to be achieved through complex hydraulic logic priority valves or complex electrical control programs. The mode only increases the system flow by increasing the number of the main valves, does not optimize the system and the main valve structure, and has the advantages of small flow capacity, large pressure loss and complex pipeline. Along with the development trend of high pressure and large flow of the hydraulic system of the mining excavator, the current combination mode of the multi-pump and the multi-loop main valve is limited by the through-flow capacity of the main valve, and the requirements of the heavy-load mining excavator cannot be met gradually.
Disclosure of Invention
The application aims to provide a hydraulic main valve and a system of a heavy-duty mining excavator, which solve the problems of weak flow capacity and poor coordination of compound actions of the main valve in the prior art.
In order to achieve the above object, the present application adopts the following technical scheme:
the hydraulic main valve of the heavy-load mining excavator comprises a confluence unit and a plurality of working units, wherein the working units comprise a first execution unit, a second execution unit, a first pilot oil path oil port, a second pilot oil path oil port, an annular oil duct and an oil return port, the confluence unit comprises a first signal screening valve and a plurality of main valve oil inlets, and the main valve oil inlets are connected with the annular oil duct;
the first execution unit comprises a first valve core assembly, an upper electromagnetic valve, a lower electromagnetic valve, a proportional priority valve, a first outer port and a second outer port, the second execution unit comprises a second valve core assembly, an upper electromagnetic valve, a lower electromagnetic valve, a proportional priority valve, a first outer port and a second outer port, the first valve core assembly and the second valve core assembly are three-position eight-way valves, an a port and a b port are respectively connected with the first outer port and the second outer port, an e port is connected with an oil return port, an f port is connected with one side input end of a first signal screening valve, an h port is connected with an oil inlet of the proportional priority valve, an oil outlet of the proportional priority valve is connected with an f port, and an output end of the first signal screening valve is connected with a control end of the proportional priority valve;
the execution joints are connected in parallel through annular oil channels: the valve core assembly g port of the execution link at the front end is connected with the c port and the d port of the execution link at the rear end, the c port and the d port of the execution link at the head end are connected with the annular oil duct, and the g port of the execution link at the tail end is connected with the oil return port;
the port A of the upper electromagnetic valve is connected with the oil tank, the port B is connected with the oil port of the first pilot oil path, and the port C is connected with the upper control end of the valve core assembly;
the port A ' of the lower electromagnetic valve is connected with the oil port of the first pilot oil way, the port B ' is connected with the oil tank, and the port C ' is connected with the lower control end of the valve core assembly;
when the first valve core assembly/the second valve core assembly works at the upper position, the port a and the port f are communicated, the port b and the port e are communicated, and the port c, the port d, the port g and the port h are communicated;
when the first valve core assembly works in the middle position, the port c, the port d and the port g are communicated, and the port e and the port f are communicated;
when the second valve core assembly works in the middle position, the port c, the port d and the port g are communicated, and the port a, the port b, the port e and the port f are communicated;
when the first valve core assembly/the second valve core assembly works in the lower position, the port a and the port e are communicated, the port b and the port f are communicated, and the port c, the port d, the port g and the port h are communicated.
Further, the valve core assembly f ports of the adjacent execution units are connected through a signal screening valve, one side input end of the signal screening valve is connected with the valve core assembly f port of the front end execution unit, the other side input end of the signal screening valve is connected with the output end of the rear end signal screening valve, the output end of the head end signal screening valve is connected with one side input end of the first signal screening valve, and one side input end of the tail end signal screening valve is directly connected with the valve core assembly f port of the tail end execution unit.
Further, a proportional bypass valve core assembly is arranged between the g port and the oil return port of the tail end execution unit, the g port of the tail end execution unit is connected with an oil inlet of the proportional bypass valve core assembly, and an oil outlet of the proportional bypass valve core assembly is connected with the oil return port.
Further, the working unit further comprises an end cover assembly, the spring cavity of the proportional bypass valve core assembly is connected with an oil outlet of the end cover assembly, and an oil inlet of the end cover assembly is connected with an oil port of the second pilot oil path.
Further, the working unit further comprises a main overflow valve, an oil inlet of the main overflow valve is connected with the annular oil duct, and an oil outlet of the main overflow valve is connected with the oil return port.
Further, the first execution unit further comprises an overload oil supplementing valve I and an overload oil supplementing valve II, an oil inlet of the overload oil supplementing valve I is connected with the first external port, and an oil outlet is connected with the oil return port; an oil inlet of the overload oil supplementing valve II is connected with a second outer port, and an oil outlet is connected with an oil return port.
The hydraulic system of the heavy-duty mining excavator comprises a movable arm oil cylinder assembly, a bucket rod oil cylinder assembly, a bucket oil cylinder assembly, a left traveling motor assembly, a rotary motor assembly, a right traveling motor assembly, an oil tank and a hydraulic main valve of the heavy-duty mining excavator;
the main valve comprises a first working link and a second working link, the first working link comprises two first execution links and one second execution link, the first execution links are respectively connected with the movable arm oil cylinder assembly and the rotary motor assembly, and the second execution links are connected with the left walking motor assembly; the second working unit comprises two first execution units and a second execution unit, the first execution units are respectively connected with the bucket rod oil cylinder assembly and the bucket oil cylinder assembly, and the second execution units are connected with the right walking motor assembly;
the two side input ends of the first signal screening valve are respectively connected with the first working link and the second working link, the main valve oil inlet is simultaneously connected with the annular oil channels of the first working link and the second working link, and the oil return ports of the first working link and the second working link are connected with the oil tank.
Further, the device also comprises a cooling pump and a cooler;
the oil inlet of the cooling pump is connected with the oil tank, and the oil outlet is connected with the cooler;
the cooler is connected with the oil return ports of the first working link and the second working link respectively, and the oil return port of the cooler is connected with the oil tank.
Further, the system also comprises a first main pump, a second main pump and a third main pump;
the oil inlets of the first main pump, the second main pump and the third main pump are connected with the oil tank, and the oil outlets are connected with the main valve oil inlets of the confluence.
Further, the hydraulic control system also comprises a pilot pump, a pilot safety control valve, a first pilot block and a second pilot block;
the pilot pump oil inlet is connected with the oil tank, the pilot pump oil outlet is connected with the pilot safety control valve oil inlet, the pilot safety control valve oil outlet is connected with the first pilot block control port, the first pilot block oil outlet is respectively connected with the control ports of the first main pump, the second main pump, the third main pump and the second pilot block, and the second pilot block oil outlet is respectively connected with the pilot oil way oil ports of the first working link and the second working link.
Further, the hydraulic control system further comprises a pilot safety valve, wherein one end of the pilot safety valve is connected with the oil outlet of the pilot pump, and the other end of the pilot safety valve is connected with the oil tank.
The application has the beneficial effects that:
by arranging the valve core valve sleeve type proportional priority valve and a signal oil way capable of carrying out load pressure screening on different execution mechanisms, screening pressure signals act on pressure compensation, load difference among different execution mechanisms can be balanced, and when proportion priority is realized, an ultra-large flow area can be realized, the requirement of an ultra-large flow system is met, and the problems of insufficient flow and poor coordination of compound actions of a hydraulic system of a heavy-duty mining excavator are effectively solved;
by arranging the proportional bypass valve, the opening of the valve core is proportionally adjusted, and pressure impact in a system is timely filtered, so that the problems of easiness in impact and poor micro-operability of a heavy-duty excavator are effectively solved, and meanwhile, when the proportional bypass valve is started, a small throttle orifice is utilized for rapid preheating, and the whole excavator acts rapidly;
by arranging the electric proportion pilot module with the reversing throttle valve core displacement feedback control, the pilot module adopts an inverse proportion decompression mode, so that the influence of hydrodynamic force generated by high pressure and large flow on the valve core movement can be reduced, and the valve core movement stability is improved;
the main valve adopts two integral working connection structures, is symmetrically distributed, is provided with a converging valve block in the middle, has compact and simple structure and few high-pressure flowing points between sheets, and effectively prolongs the service life of the main valve;
the universal valve body structure is designed, the universal valve body structure can be used for opening the central main valve and closing the central main valve, is suitable for different systems such as load sensitivity, positive flow, full electric control independent control and the like, is designed in an interchangeable control mode, has the interchangeable functions of hydraulic control and integrated electric control, and has strong main valve applicability;
by adopting the design of a three-pump and single-loop system, the method changes the mode of confluence oil supply after double valve cores or three valve core valves of a bucket rod, a bucket, a movable arm and the like of the traditional mining excavator hydraulic system, and respectively sets the confluence oil supply before the single valve core valves, thereby greatly reducing the use of a system priority valve and a logic valve, simplifying the hydraulic system, improving the reliability of the system and meeting the flow requirement of a 100-200 ton heavy-duty excavator.
Drawings
FIG. 1 is a schematic diagram of an excavator hydraulic system of the present application;
FIG. 2 is a hydraulic schematic of the main valve of the present application;
FIG. 3 is a first work junction and junction composition of the present application;
FIG. 4 is a second embodiment of the present application of a bonding pattern;
FIG. 5 is a second work coupling pattern of the present application;
FIG. 6 is a main valve outline view of the present application;
FIG. 7 is a first structural cross-sectional view of the main valve of the present application;
FIG. 8 is a second structural cross-sectional view of the main valve of the present application;
fig. 9 is a first performing bonding pattern of the present application.
Meaning of reference numerals in the drawings: 1-a first main pump; 2-a second main pump; 3-a third main pump; 4-a cooling pump; 5-a pilot pump; 6-a pilot safety valve; 7-a pilot safety control valve; an 8-cooler; 9-a first guide block; 10-a second guide block; 11-a main valve; 11.1-a first signal screen valve; 11.2-a main overflow valve; 11.3-boom spool assembly; 11.4-a rotary spool assembly; 11.5-left traveling valve core assembly; 11.6-a first proportional bypass spool assembly; 11.7-a first overload oil replenishment valve; 11.8-a second overload oil replenishment valve; 11.9-a first proportional priority valve; 11.10-a second proportional priority valve; 11.11-a third proportional priority valve; 11.12-a second signal screen valve; 11.13-a third signal screen valve; 11.14—a first solenoid valve; 11.15-a second solenoid valve; 11.16-a third solenoid valve; 11.17-a first reverse ratio pilot cap assembly; 11.18-a second inverse pilot cap assembly; 11.19-fourth solenoid valve; 11.20-fifth solenoid valve; 11.21-sixth solenoid valve; 11.22-a first end cap assembly; 11.23-bucket rod valve core assembly; 11.24-bucket spool assembly; 11.25-right travelling valve core assembly; 11.26—a second proportional bypass spool assembly; 11.27-a third overload oil replenishment valve; 11.28-fourth overload oil compensating valve; 11.29-a fifth overload oil make-up valve; 11.30-sixth overload oil replenishment valve; 11.31-fourth proportional priority valve; 11.32-a fifth proportional priority valve; 11.33-a sixth proportional priority valve; 11.34-fourth signal screen valve; 11.35-a fifth signal screen valve; 11.36-seventh solenoid valve; 11.37-eighth solenoid valve; 11.38-ninth solenoid valve; 11.39-third proportional pilot end cap assembly; 11.40-tenth solenoid valve; 11.41-eleventh solenoid valve; 11.42-twelfth solenoid valve; 11.43-fourth inverse pilot cap assembly; 11.44-a second end cap assembly; 12-a movable arm oil cylinder assembly; 13-a bucket rod oil cylinder assembly; 14-a bucket cylinder assembly; 15-left travel motor assembly; 16-a rotary motor assembly; 17-right travel motor assembly; 18-oil tank.
Detailed Description
The following detailed description of the technical solutions of the present application will be given by way of the accompanying drawings and specific embodiments, and it should be understood that the specific features of the embodiments and embodiments of the present application are detailed descriptions of the technical solutions of the present application, and not limiting the technical solutions of the present application, and that the embodiments and technical features of the embodiments of the present application may be combined with each other without conflict.
Example 1
The embodiment discloses a hydraulic main valve of a heavy-duty mining excavator, as shown in fig. 2, a main valve 11 is of an integral structure and comprises a confluence joint and a plurality of working joints. Each working unit comprises a plurality of first execution units, a plurality of second execution units, a first pilot oil path oil port, a second pilot oil path oil port, an annular oil duct, an oil return port, a proportional bypass valve core assembly, a main overflow valve, a signal screening valve and an end cover assembly.
The second execution unit provides an oil source for the excavator travelling mechanism, and as shown in fig. 4, the second execution unit comprises a second valve core assembly, an upper electromagnetic valve, a lower electromagnetic valve and a proportional priority valve. The valve core assembly is a three-position eight-way valve, an a port and a b port are respectively connected with a first outer port and a second outer port, the first outer port and the second outer port are respectively used for being externally connected with two ends of an executing mechanism, the executing mechanism can be a motor or an oil cylinder, an e port is connected with an oil return port, an f port is connected with one side input end of a first signal screening valve 11.1, an h port is connected with an oil inlet of a proportional priority valve, an oil outlet of the proportional priority valve is connected with an f port, and an output end of the first signal screening valve 11.1 is connected with a control end of the proportional priority valve. The port A of the upper electromagnetic valve is connected with the oil tank, the port B is connected with the oil port of the first pilot oil path, and the port C is connected with the upper control end of the valve core assembly. The port A ' of the lower electromagnetic valve is connected with the oil port of the first pilot oil way, the port B ' is connected with the oil tank, and the port C ' is connected with the lower control end of the valve core assembly. When the second execution valve core assembly works at the upper position, the port a and the port f are communicated, the port b and the port e are communicated, and the port c, the port d, the port g and the port h are communicated; when the second execution valve core assembly works in the middle position, the port c, the port d and the port g are communicated, and the port a, the port b, the port e and the port f are communicated; when the second execution valve core assembly works at the lower position, the port a and the port e are communicated, the port b and the port f are communicated, and the port c, the port d, the port g and the port h are communicated
The first execution unit provides an oil supply for a working device of the excavator, and the working device comprises a rotary arm, a movable arm, a bucket rod, a bucket and the like. The first execution unit and the second execution unit are different only in that when the valve core assemblies of the first execution unit and the second execution unit are in the middle position, the oil ports are communicated in different modes. As shown in fig. 9, when the first spool assembly of the first execution unit is operated at the neutral position, the c port, the d port and the g port are communicated, and the e port and the f port are communicated.
The first execution unit further comprises an overload oil supplementing valve I and an overload oil supplementing valve II, an oil inlet of the overload oil supplementing valve I is connected with the first external port, and an oil outlet is connected with the oil return port; the second oil inlet of the overload oil supplementing valve is connected with the second outer port, and the oil outlet is connected with the oil return port.
All execution units are connected in parallel through annular oil channels: the valve core assembly g port of the execution unit at the front end is connected with the c port and the d port of the rear end, the c port and the d port of the execution unit at the head end are connected with the annular oil duct, and the g port of the execution unit at the tail end is connected with the oil return port. A proportional bypass valve core assembly is further arranged between the g port and the oil return port of the tail end traveling assembly, the g port of the tail end traveling assembly is connected with an oil inlet of the proportional bypass valve core assembly, and an oil outlet of the proportional bypass valve core assembly is connected with the oil return port. The spring cavity of the proportional bypass valve core assembly is connected with the oil outlet of the end cover assembly, and the oil inlet of the end cover assembly is connected with the oil port of the second pilot oil way.
The valve core assembly f ports of the adjacent execution units are connected through a signal screening valve, one side input end of the front end signal screening valve is connected with the valve core assembly f port of the front end execution unit, the other side input end of the front end signal screening valve is connected with the output end of the rear end signal screening valve, the output end of the head end signal screening valve is connected with one side input end of the first signal screening valve 11.1, and one side input end of the tail end signal screening valve is directly connected with the valve core assembly f port of the tail end execution unit.
An oil inlet of the main overflow valve is connected with the annular oil duct, and an oil outlet of the main overflow valve is connected with the oil return port.
The present embodiment is described with a first work unit, a second work unit, and a confluence unit:
the first working unit is shown in fig. 3, and comprises a left walking executing unit, a rotation executing unit, a movable arm executing unit, a pilot oil passage port Pf1, a pilot oil passage port Pf3, an annular oil passage Pc1, an oil return port T1, a first proportional bypass valve core assembly 11.6, a main relief valve 11.2, a second signal screening valve 11.12, a third signal screening valve 11.13 and a first end cover assembly 11.22. The left walking execution unit comprises a left walking valve core assembly 11.5, a third electromagnetic valve 11.16, a sixth electromagnetic valve 11.21, a third proportional priority valve 11.11, an At1 port and a Bt1 port. The rotary execution unit comprises a rotary valve core assembly 11.4, a second electromagnetic valve 11.15, a fifth electromagnetic valve 11.20, a second proportional priority valve 11.10, an As port and a Bs port. The movable arm execution link comprises a movable arm valve core assembly 11.3, a first electromagnetic valve 11.14, a fourth electromagnetic valve 11.19, a first proportional priority valve 11.9, a first overload oil supplementing valve 11.7, a second overload oil supplementing valve 11.8, a Bb1 port and an Ab1 port.
The second working unit is shown in fig. 5, and comprises a bucket rod execution unit, a bucket execution unit, a right walking execution unit, a pilot oil passage port Pf2, a pilot oil passage port Pf4, an annular oil passage Pc2, an oil return port T2, a second proportional bypass valve core assembly 11.26, a fourth signal screening valve 11.34, a fifth signal screening valve 11.35 and a second end cover assembly 11.44. The bucket rod execution unit comprises a bucket rod valve core assembly 11.23, a seventh electromagnetic valve 11.36, a tenth electromagnetic valve 11.40, a third overload oil supplementing valve 11.27, a fourth overload oil supplementing valve 11.28 and a fourth proportion priority valve 11.31. The bucket execution unit comprises a bucket valve core assembly 11.24, an eighth electromagnetic valve 11.37, an eleventh electromagnetic valve 11.41, a fifth overload oil supplementing valve 11.29, a sixth overload oil supplementing valve 11.30 and a fifth proportion priority valve 11.32. The right walking execution unit comprises a right walking valve core assembly 11.25, a ninth electromagnetic valve 11.38, a twelfth electromagnetic valve 11.42 and a sixth proportional priority valve 11.33.
The confluence is shown in fig. 3, and mainly comprises main valve oil inlets P1, P2 and P3, a first signal screening valve 11.1 and three pump confluence oil channels.
The hydraulic system provides that the pilot oil enters the first inverse proportion pilot end cover assembly 11.17, the second inverse proportion pilot end cover assembly 11.18, the third inverse proportion pilot end cover assembly 11.39, the fourth inverse proportion pilot end cover assembly 11.43, the first electromagnetic valve 11.14, the second electromagnetic valve 11.15, the third electromagnetic valve 11.16, the fourth electromagnetic valve 11.19, the fifth electromagnetic valve 11.20, the sixth electromagnetic valve 11.21, the seventh electromagnetic valve 11.36, the eighth electromagnetic valve 11.37, the ninth electromagnetic valve 11.38, the tenth electromagnetic valve 11.40, the eleventh electromagnetic valve 11.41 and the twelfth electromagnetic valve 11.42 through the pilot oil ports Pf1 and Pf2, acts on two ends of the valve core assembly, and when the electromagnetic valves do not have control current input, the valve core assembly is in the middle position under the action of the pilot oil on two sides. At this time, even if pressure pulsation exists to a certain extent in the system, the two ends of the valve core can still be kept at the middle position under the acting force of high-pressure pilot oil, and the middle position stability is good. Additionally, pilot oil enters the spring chambers of the first proportional bypass spool assembly 11.6 and the second proportional bypass spool assembly 11.26 through pilot oil inlets Pf3, pf4 in the first end cap assembly 11.22 and the second end cap assembly 11.44.
Oil provided by a first main pump 1, a second main pump 2 and a third main pump 3 of the system enters a first working joint annular oil duct Pc1 and a second working joint annular oil duct Pc2 through a combined flow joint oil duct, and when the engine is started, the oil is quickly preheated through a 11.6 small throttle opening of a first proportional bypass valve core assembly, so that the whole engine acts quickly; when the main machine performs compound actions such as falling of a movable arm, adduction of a bucket, a control current signal is input to the fourth electromagnetic valve 11.19, the seventh electromagnetic valve 11.36 and the eleventh electromagnetic valve 11.41, the proportion of pilot pressure XBb, XAa, XBc of the electromagnetic valves is reduced under the action of the current signal, at the moment, the movable arm, the bucket rod and the bucket valve core move under the action of pilot oil pressure difference at two sides, the movable arm, the bucket rod and the bucket valve core are respectively in an upper position, a lower position and an upper position, high-pressure oil provided by a main pump enters the first proportion priority valve 11.9, the fourth proportion priority valve 11.31 and the fifth proportion priority valve 11.32 after passing through throttle openings of the movable arm, the bucket rod and the bucket valve core and then enters corresponding executing mechanisms, the load pressure of an actuating mechanism is used as a signal to be introduced into a third signal screening valve 11.13, a fourth signal screening valve 11.34 and a fifth signal screening valve 11.35, the highest pressure signal is screened out by the first signal screening valve 11.1 and is respectively introduced into control ends of a first proportional priority valve 11.9, a fourth proportional priority valve 11.31 and a fifth proportional priority valve 11.32, so that loop pressures of a movable arm, a bucket rod and a bucket actuating mechanism are similar, flow distribution is determined by opening degrees of throttle openings of respective valve cores, and in addition, the screened pressure signals are simultaneously acted with the first main pump 1, the second main pump 2 and the third main pump 3 and are used for regulating the discharge capacity of the main pumps. When the valve core is opened or closed rapidly, the system can generate higher impact pressure, at the moment, the pilot currents of the first proportional bypass valve core assembly 11.6 and the second proportional bypass valve core assembly 11.26 of the proportional bypass valve are regulated, the opening of the proportional bypass valve core is regulated, the excessive flow caused by impact in the system is unloaded in time, the pressure impact in the system is filtered, and the operability of the host is improved.
With reference to fig. 6 to 8, the first working unit, the confluence unit and the second working unit are sequentially arranged from left to right, and in some cases, the first working unit and the second working unit can be independently used as a main valve. The first working link has the functions of controlling the ascending and descending of the movable arm, the forward rotation and reverse rotation of the rotation and the forward and reverse rotation of the left walking, and is provided with a main overflow valve 11.2 for limiting the highest working pressure of the system, preventing the system and elements from being damaged due to the overhigh pressure and playing a role of a safety valve; the first overload oil compensating valve 11.7 and the second overload oil compensating valve 11.8 are arranged to prevent the overload of the actuating mechanism from damaging elements, and the oil in a cavity with too low pressure in the actuating mechanism can be timely compensated to prevent suction; an annular oil duct Pc1 is arranged and is connected with a converging combined flow oil duct; an oil return port T1 is arranged, and the oil return tank 18 is led from the port T1 after the oil return of the first working link is converged; the first proportional priority valve 11.11, the second proportional priority valve 11.12 and the third proportional priority valve 11.13 are arranged and are used for proportionally distributing the required flow of each executing mechanism during the compound action, and the proportional priority valves adopt a valve core and valve sleeve structure, so that the pressure loss is reduced, and the high-pressure large flow is realized; the hydraulic oil system is provided with a second signal screening valve 11.12 and a third signal screening valve 11.13, wherein the second signal screening valve 11.12 is used for comparing the pressure of the left walking U-shaped oil duct with the pressure of the rotary U-shaped oil duct, and the third signal screening valve 11.13 is used for comparing the pressure output by the movable arm U-shaped oil duct with the pressure output by the second signal screening valve 11.12; a first proportional bypass spool assembly 11.6 is provided for controlling warm-up and shock of the hydraulic system.
The second working link has the functions of controlling the adduction and the external swinging of the bucket rod, the adduction and the external swinging of the bucket and the forward and backward movement of the right walking, and is provided with a third overload oil supplementing valve 11.27, a fourth overload oil supplementing valve 11.28, a fifth overload oil supplementing valve 11.29 and a sixth overload oil supplementing valve 11.30, so that the overload of an actuating mechanism is prevented, the damage of elements is prevented, and the oil in a cavity with too low pressure in the actuating mechanism can be timely supplemented, so that the suction is prevented; an annular oil duct Pc2 is arranged and is connected with a converging combined flow oil duct; an oil return port T2 is arranged, and the oil return tank 18 is led from the port T2 after the oil return of the second working link is converged; a fourth proportional priority valve 11.31, a fifth proportional priority valve 11.32 and a sixth proportional priority valve 11.33 are arranged for proportionally distributing the required flow of each executing mechanism during the compound action; the hydraulic system is provided with a fourth signal screening valve 11.34 and a fifth signal screening valve 11.35, wherein the fourth signal screening valve 11.34 is used for comparing the pressure of the right walking U-shaped oil duct and the bucket U-shaped oil duct, and the fifth signal screening valve 11.35 is used for comparing the pressure output by the bucket rod U-shaped oil duct and the fourth signal screening valve 11.34; a second proportional bypass spool assembly 11.26 is provided for controlling warm-up and shock of the hydraulic system.
The converging connection has the functions of completing the converging of the first main pump 1, the second main pump 2 and the third main pump 3, arranging oil inlets P1, P2 and P3 of a main valve 11, enabling high-pressure oil output by the first main pump 1, the second main pump 2 and the third main pump 3 to enter a converging joint flow oil passage through the oil inlets P1, P2 and P3, and enabling the oil to enter a first working joint annular oil passage Pc1 and a second working joint annular oil passage Pc2 of the main valve 11 after converging; a first signal screening valve 11.1 is provided for comparing the pressures of the first and second working branches and applying the highest pressure to the first proportional priority valve 11.9, the second proportional priority valve 11.10, the third proportional priority valve 11.11, the fourth proportional priority valve 11.31, the fifth proportional priority valve 11.32, the sixth proportional priority valve 11.33.
Fig. 7 and 8 are cross-sectional views of the main valve 11. Referring to fig. 6-8, the pressure oil provided by the three main pumps enters the first working joint annular oil duct Pc1 and the second working joint annular oil duct Pc2 after combined flow, the first working joint annular oil duct Pc1 is communicated with the oil return port T1 through the first proportional bypass valve core assembly 11.6, and the second working joint annular oil duct Pc2 is communicated with the oil return port T2 through the second proportional bypass valve core assembly 11.26. Because Pc1 and Pc2 are annular oil ducts, when the valve core of the actuating mechanism changes direction, the main pump flow can be ensured to be respectively connected with the oil return ports T1 and T2 through the first proportional bypass valve core assembly 11.6 and the second proportional bypass valve core assembly 11.26.
Example two
The embodiment discloses a heavy-duty mining excavator hydraulic system, and the hydraulic system is applied with the main valve, as shown in fig. 1, and comprises: the hydraulic control system comprises a first main pump 1, a second main pump 2, a third main pump 3, a cooling pump 4, a pilot pump 5, a pilot safety valve 6, a pilot safety control valve 7, a cooler 8, a first pilot block 9, a second pilot block 10, a main valve 11, a movable arm cylinder assembly 12, a bucket rod cylinder assembly 13, a bucket cylinder assembly 14, a left traveling motor assembly 15, a rotary motor assembly 16, a right traveling motor assembly 17 and an oil tank 18. The first main pump 1, the second main pump 2, and the third main pump 3 are joined in a joint of the main valves 11, and supply pressure oil to the main valves 11 together, thereby forming a multi-pump single-circuit system.
The cooling pump 4 carries out temperature control to main valve oil return through the cooler 8, and the oil return opening is connected to the cooler 8, and when the system temperature is too high, cooling pump 4 opens, and when the system oil temperature is in normal range, cooling pump 4 closes, and fluid directly returns to the oil tank.
The pilot pump 5 provides the pilot oil to the first pilot block 9 and the second pilot block 10 respectively, so as to control the valve cores of the main valve 11 to change direction, and simultaneously the pilot pump 5 provides the pilot oil to the first pilot block 9 and the second pilot block 10 respectively, so as to control the first main pump 1, the second main pump 2, the third main pump 3, the left traveling motor assembly 15, the rotary motor assembly 16 and the right traveling motor assembly 17 to change the displacement. The pilot oil enters the pilot oil ports Pf1, pf2, pf3 and Pf4 of the main valve 11 through the second pilot block 10, and the switching of the valve element is controlled by the on-off of the pilot current, thereby completing the corresponding operation.
The pilot relief valve 6 sets the highest pressure of the pilot system, preventing overload of the pilot oil passage. The pilot safety control valve 7 controls the on-off of the pilot oil way of the main valve 11, and plays a role in safety protection. The pilot safety control valve 7 is a normally-closed solenoid valve, and the pilot oil way of the main valve 11 is cut off in a default state, at this time, even if the host is operated, the control valve cores of all the actuating mechanisms are still in a static state because the pilot oil can not be obtained for reversing, so that safety accidents caused by misoperation are prevented, when the host is required to work, the pilot safety control valve 7 is powered on, and the pilot oil provided by the pilot pump 5 reaches the first pilot block 9 and the second pilot block 10, so that the host is controlled to complete corresponding actions.
The foregoing is merely a preferred embodiment of the present application, and it should be noted that modifications and variations could be made by those skilled in the art without departing from the technical principles of the present application, and such modifications and variations should also be regarded as being within the scope of the application.
Claims (11)
1. The hydraulic main valve of the heavy-load mining excavator is characterized by comprising a confluence joint and a plurality of working joints, wherein the working joints comprise a first execution joint, a second execution joint, a first pilot oil way oil port, a second pilot oil way oil port, an annular oil duct and an oil return port, the confluence joint comprises a first signal screening valve (11.1) and a plurality of main valve oil inlets, and the main valve oil inlets are connected with the annular oil duct;
the first execution unit comprises a first valve core assembly, an upper electromagnetic valve, a lower electromagnetic valve, a proportional priority valve, a first outer port and a second outer port, the second execution unit comprises a second valve core assembly, an upper electromagnetic valve, a lower electromagnetic valve, a proportional priority valve, a first outer port and a second outer port, the first valve core assembly and the second valve core assembly are three-position eight-way valves, an a port and a b port are respectively connected with the first outer port and the second outer port, an e port is connected with an oil return port, an f port is connected with one side input end of a first signal screening valve (11.1), an h port is connected with an oil inlet of the proportional priority valve, an oil outlet of the proportional priority valve is connected with an f port, and an output end of the first signal screening valve (11.1) is connected with a control end of the proportional priority valve;
the execution units are connected in parallel through annular oil channels: the valve core assembly g port of the execution link at the front end is connected with the c port and the d port of the execution link at the rear end, the c port and the d port of the execution link at the head end are connected with the annular oil duct, and the g port of the execution link at the tail end is connected with the oil return port;
an opening A of the upper electromagnetic valve is connected with an oil tank, an opening B of the upper electromagnetic valve is connected with a first pilot oil path oil port, and an opening C of the upper electromagnetic valve is connected with an upper control end of the valve core assembly;
the port A ' of the lower electromagnetic valve is connected with the oil port of the first pilot oil way, the port B ' is connected with the oil tank, and the port C ' is connected with the lower control end of the valve core assembly;
when the first valve core assembly/the second valve core assembly works at the upper position, the port a and the port f are communicated, the port b and the port e are communicated, and the port c, the port d, the port g and the port h are communicated;
when the first valve core assembly works in the middle position, the port c, the port d and the port g are communicated, and the port e and the port f are communicated;
when the second valve core assembly works in the middle position, the port c, the port d and the port g are communicated, and the port a, the port b, the port e and the port f are communicated;
when the first valve core assembly/the second valve core assembly works in the lower position, the port a and the port e are communicated, the port b and the port f are communicated, and the port c, the port d, the port g and the port h are communicated.
2. The hydraulic main valve of the heavy-duty mining excavator according to claim 1, wherein f ports of the valve core assemblies of the adjacent execution units are connected through a signal screening valve, one side input end of the signal screening valve is connected with f ports of the valve core assemblies of the front execution units, the other side input end of the signal screening valve is connected with the output end of the rear signal screening valve, the output end of the head signal screening valve is connected with one side input end of the first signal screening valve (11.1), and one side input end of the tail signal screening valve is directly connected with f ports of the valve core assemblies of the tail execution units.
3. The hydraulic main valve of the heavy-duty mining excavator according to claim 1, wherein a proportional bypass valve core assembly is further arranged between a g port and an oil return port of the end execution unit, the g port of the end execution unit is connected with an oil inlet of the proportional bypass valve core assembly, and an oil outlet of the proportional bypass valve core assembly is connected with the oil return port.
4. The heavy-duty mining excavator hydraulic main valve of claim 3 wherein the work unit further comprises an end cap assembly, the proportional bypass spool assembly spring cavity being connected to an end cap assembly oil outlet, the end cap assembly oil inlet being connected to a second pilot oil port.
5. The heavy-duty mining excavator hydraulic main valve of claim 1 wherein the work unit further comprises a main relief valve, an oil inlet of the main relief valve being connected to the annular oil gallery, and an oil outlet being connected to the oil return port.
6. The hydraulic main valve of the heavy-duty mining excavator according to claim 1, wherein the first execution unit further comprises an overload oil supplementing valve I and an overload oil supplementing valve II, an oil inlet of the overload oil supplementing valve I is connected with a first outer port, and an oil outlet is connected with an oil return port; and an oil inlet of the overload oil supplementing valve II is connected with a second external port, and an oil outlet is connected with an oil return port.
7. A hydraulic system of a heavy-duty mining excavator, which is characterized by comprising a movable arm oil cylinder assembly (13), a bucket rod oil cylinder assembly (13), a bucket oil cylinder assembly (14), a left traveling motor assembly (15), a rotary motor assembly (16), a right traveling motor assembly (17), an oil tank (18) and the hydraulic main valve of the heavy-duty mining excavator according to any one of claims 1-6;
the main valve comprises a first working link and a second working link, the first working link comprises two first execution links and one second execution link, the first execution links are respectively connected with the movable arm oil cylinder assembly (12) and the rotary motor assembly (16), and the second execution links are connected with the left walking motor assembly (15); the second working unit comprises two first execution units and a second execution unit, the first execution units are respectively connected with the bucket rod oil cylinder assembly (13) and the bucket oil cylinder assembly (14), and the second execution units are connected with the right walking motor assembly (17);
the two-side input ends of the first signal screening valve (11.1) are respectively connected with a first working unit and a second working unit, the main valve oil inlet is simultaneously connected with annular oil channels of the first working unit and the second working unit, and the oil return openings of the first working unit and the second working unit are connected with an oil tank (18).
8. The heavy-duty mining excavator hydraulic system of claim 7 further comprising a cooling pump (4), a cooler (8);
an oil inlet of the cooling pump (4) is connected with an oil tank (18), and an oil outlet of the cooling pump is connected with a cooler (8);
the cooler (8) is respectively connected with oil return ports of the first working unit and the second working unit, and the oil return port of the cooler (8) is connected with the oil tank (18).
9. The heavy-duty mining excavator hydraulic system of claim 7 further comprising a first main pump (1), a second main pump (2), a third main pump (3);
and oil inlets of the first main pump (1), the second main pump (2) and the third main pump (3) are connected with an oil tank (18), and oil outlets are connected with oil inlets of main valves in a confluence manner.
10. The heavy-duty mining excavator hydraulic system of claim 9 further comprising a pilot pump (5), a pilot safety control valve (7), a first pilot block (9), a second pilot block (10);
the oil inlet of the pilot pump (5) is connected with the oil tank (18), the oil outlet of the pilot pump (5) is connected with the oil inlet of the pilot safety control valve (7), the oil outlet of the pilot safety control valve (7) is connected with the control port of the first pilot block (9), the oil outlet of the first pilot block (9) is respectively connected with the control ports of the first main pump (1), the second main pump (2), the third main pump (3) and the second pilot block (10), and the oil outlet of the second pilot block (10) is respectively connected with the pilot oil way oil ports of the first working link and the second working link.
11. The heavy-duty mining excavator hydraulic system according to claim 10, further comprising a pilot relief valve (6), wherein one end of the pilot relief valve (6) is connected to an oil outlet of the pilot pump (5), and one end is connected to an oil tank (18).
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