CN204985186U - Automatically controlled switching core hydraulic system and engineering machinery - Google Patents

Automatically controlled switching core hydraulic system and engineering machinery Download PDF

Info

Publication number
CN204985186U
CN204985186U CN201520653048.2U CN201520653048U CN204985186U CN 204985186 U CN204985186 U CN 204985186U CN 201520653048 U CN201520653048 U CN 201520653048U CN 204985186 U CN204985186 U CN 204985186U
Authority
CN
China
Prior art keywords
valve
hydraulic
valve block
oil
control
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn - After Issue
Application number
CN201520653048.2U
Other languages
Chinese (zh)
Inventor
谢朝阳
沈勇
任大明
张安民
马鹏鹏
赵梅
王苏东
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Technology Branch of XCMG Engineering Machinery Co Ltd
Original Assignee
Technology Branch of XCMG Engineering Machinery Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Technology Branch of XCMG Engineering Machinery Co Ltd filed Critical Technology Branch of XCMG Engineering Machinery Co Ltd
Priority to CN201520653048.2U priority Critical patent/CN204985186U/en
Application granted granted Critical
Publication of CN204985186U publication Critical patent/CN204985186U/en
Withdrawn - After Issue legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Abstract

The utility model relates to an automatically controlled switching core hydraulic system, including being used for for the constant delivery pump system of at least one actuating mechanism fuel feeding, a variable pump system for being at least one the 2nd actuating mechanism fuel feeding, switching core control valve block and the electric liquid control valve block who is connected with switching core control valve block, electrohydraulic control valve piece can turn into the liquid accuse instruction that is used for controlling switching core control valve block's opening size with the automatically controlled instruction of received, the switching core control valve block connect on the oil circuit between constant delivery pump system and variable pump system, with the switching through switching core control valve block, make variable pump system perhaps to be at least one the 2nd actuating mechanism fuel feeding for at least one actuating mechanism alone with at least one the 2nd actuating mechanism fuel feeding simultaneously. The utility model discloses still relate to an engineering machinery. Switching core control valve block's opening size graduallys change among the automatically controlled switching core hydraulic system, can overcome the compression shock of intersystem, improves the controllability of system.

Description

A kind of automatically controlled opening and closing core hydraulic system and engineering machinery
Technical field
The utility model relates to technical field of engineering machinery, particularly relates to a kind of automatically controlled opening and closing core hydraulic system and engineering machinery.
Background technique
Widely, different purposes and complicated operating mode determine the complexity of its hydraulic work system to the purposes of engineering machinery.Construction machinery hydraulic system common at present has quantitative system, quantitative and set of variables assembly system and entire variable system etc.Existing quantitative and set of variables assembly system, the hydraulic oil of its working cell is by metering pump fuel feeding together with variable displacement pump, and when in system, the demand of hydraulic oil is larger, the oil pump capacity of variable displacement pump increases; When in system, the demand of hydraulic oil is less, the oil pump capacity of variable displacement pump reduces, and variable displacement pump has the function of regulating system fuel delivery.But when the demand of system to hydraulic oil is less than the fuel delivery of metering pump, metering pump cannot play the function of adjusting oil mass, and system parenchyma is full quantitative system, at this moment internal system energy loss is larger, and energy saving of system effect is undesirable.
At present, the fine motion of user to complete machine is more and more paid attention to, existing fine motion that is quantitative and set of variables assembly system is poor, its converging valve block many employings switch valve controls, when there is pressure difference between Constant Pump System and variable pump systems, converging valve block directly jumps to full open position by closed condition, huge impact can be caused like this to two systems, thus cause the damage of associated components, make the energy loss of fluid also larger, therefore when some operating mode needs to finely tune equipment, existing quantitatively and set of variables assembly system cannot meet usage requirement.
In addition, due in whole working, there is fluctuation in oil cylinder internal pressure, cause the pressure of pumping hole to change thereupon.When pump intake pressure fluctuation exceeds certain scope, unloading valve can open and close repeatedly, causes the discontinuous of complete machine action, excites the shake of complete machine simultaneously, and produces noise.The common working pump unloading valve block quantitatively and in set of variables assembly system, its speed opened and closed is uncontrollable, so impact comparatively large, off-load is unstable.In general opening and closing core system working procedure, when especially spool opens and closes, system shock pressure is comparatively large, constrains the working life of machine system and each element.
Model utility content
The purpose of this utility model proposes a kind of automatically controlled opening and closing core hydraulic system and engineering machinery, to enable automatically controlled opening and closing core hydraulic system overcome compression shock between system, improves the controllability of system.
For achieving the above object, the utility model provides a kind of automatically controlled opening and closing core hydraulic system, comprise for the Constant Pump System at least one first actuator's fuel feeding, for the variable pump systems at least one second actuator's fuel feeding, opening and closing core control valve block and the electro-hydraulic control valve block be connected with described opening and closing core control valve block, the automatically controlled instruction morphing hydraulic control instruction for being used for the openings of sizes controlling described opening and closing core control valve block that described electro-hydraulic control valve block can will receive, described opening and closing core control valve block is connected on the connection oil circuit between described Constant Pump System and described variable pump systems, with the opening and closing by described opening and closing core control valve block, make described variable pump systems can simultaneously at least one first actuator described and at least one second actuator's fuel feeding described or be separately at least one second actuator's fuel feeding described.
Further, also comprise electric control handle and controller, described controller can receive the stick control signal that described electric control handle exports, and sends described automatically controlled instruction according to described stick control signal to described electro-hydraulic control valve block.
Further, also comprise the unloading valve block on the working connection being connected to described Constant Pump System, described electro-hydraulic control valve block is provided with the hydraulic fluid port P9 be communicated with described unloading valve block, described controller can control described electro-hydraulic control valve block and carry out pressure off-load by described unloading valve block to described Constant Pump System.
Further, also comprise the mode of operation diverter switch be connected with described controller, described controller can receive the output order of described mode of operation diverter switch, and controls described electro-hydraulic control valve block according to described output order.
Further, described controller when detecting that at least one first actuator described moves to the end of travel preset length apart from least one the first actuator described, can control described electro-hydraulic control valve block and carrying out pressure off-load by described unloading valve block to described Constant Pump System.
Further, described unloading valve block comprises first segment discharge orifice, cartridge valve and relief valve, the hydraulic fluid port A of described cartridge valve is communicated with the first oil inlet P 5 be arranged on described unloading valve block, the hydraulic fluid port B of described cartridge valve is communicated with the oil return inlet T 5 be arranged on described unloading valve block, described first segment discharge orifice is connected between described first oil inlet P 5 and the control port X of described cartridge valve, described relief valve is arranged between the control port X of described cartridge valve and described oil return inlet T 5, and the hydraulic fluid port P9 on described electro-hydraulic control valve block is connected with the control port X of described cartridge valve.
Further, described unloading valve block also comprises second section discharge orifice, described second section discharge orifice is arranged between the control port X of described cartridge valve and described relief valve, for controlling the movement velocity of the spool of described cartridge valve, prevent described spool from the opening procedure of control port X, clashing into the valve seat of described cartridge valve.
Further, described unloading valve block also comprises the 3rd throttle orifice between hydraulic fluid port A and described first oil inlet P 5 and the first one-way valve that are parallel to described cartridge valve, for controlling the movement velocity of the spool of described cartridge valve, prevent described spool from the closing process of hydraulic fluid port A, clashing into the valve seat of described cartridge valve, and hydraulic oil can be avoided the impact of described first oil inlet P 5 place oil pipe.
Further, also comprise pilot control block, described pilot control block is by the variable displacement pump fuel feeding in described variable pump systems, and for described electro-hydraulic control valve block provide pilot control oil, described controller is connected with described pilot control block, and controls the break-make of described pilot control block to the oil circuit of described electro-hydraulic control valve block fuel feeding.
Further, be provided with solenoid directional control valve in described pilot control block, described controller controls the break-make of described pilot control block to the oil circuit of described electro-hydraulic control valve block fuel feeding by the break-make controlling described solenoid directional control valve.
Further, also comprise pilot-actuated valve, described pilot-actuated valve is for screening load pressure signal larger at least one first actuator described and at least one second actuator described, and feed back to the variable control mechanism of variable displacement pump in described variable pump systems as load feedback signal, and then control the oil pump capacity of described variable displacement pump.
Further, described pilot-actuated valve comprises shuttle valve and the 4th throttle orifice, two filler openings of described shuttle valve are respectively used to the load pressure signal receiving at least one first actuator described and at least one the second actuator described, and described 4th throttle orifice is between the oil outlet and the outlet of described pilot-actuated valve of described shuttle valve.
Further, also comprise constant difference overflow valve, the filler opening of described constant difference overflow valve is communicated with the oil outlet of described variable displacement pump, and the oil outlet of described constant difference overflow valve is communicated with fuel tank, the spring chamber of described constant difference overflow valve and the outlet of described pilot-actuated valve.
Further, at least one first actuator described comprises tipping bucket cylinder and swing arm cylinder, distributing valve is provided with in described Constant Pump System, described electro-hydraulic control valve block is provided with the hydraulic fluid port that at least one valve core movement for described distributing valve provides pilot control oil, described distributing valve, for controlling the action of described tipping bucket cylinder and described swing arm cylinder, described distributing valve is provided with the hydraulic fluid port P3 be connected with described opening and closing core control valve block.
Further, at least one second actuator described comprises left steering oil cylinder and right steering oil cylinder, commutator and flux amplification valve is provided with in described variable pump systems, described commutator is for controlling described flux amplification valve, and the action of described left steering oil cylinder and described right steering oil cylinder is controlled by described flux amplification valve, described flux amplification valve is provided with the hydraulic fluid port EF be connected with described opening and closing core control valve block.
Further, the oil return circuit of described Constant Pump System is disposed with the hydraulic oil radiator for dispelling the heat to hydraulic oil and the oil return filter cleaner for filtering hydraulic oil, the oil return inlet T 5 of described unloading valve block is connected between the outlet of described hydraulic oil radiator and the filler opening of described oil return filter cleaner.
For achieving the above object, the utility model additionally provides a kind of engineering machinery, comprises the automatically controlled opening and closing core hydraulic system in the various embodiments described above.
Based on technique scheme, the utility model by arranging opening and closing core control valve block between Constant Pump System and variable pump systems, and controlled according to the openings of sizes of automatically controlled instruction to opening and closing core control valve block received by electro-hydraulic control valve block, can make variable pump systems can simultaneously at least one second actuator and at least one first actuator's fuel feeding or be separately at least one second actuator's fuel feeding.Because opening and closing core control valve block can adjust its openings of sizes according to actual needs, therefore when needs variable pump systems be simultaneously at least one second actuator and at least one first actuator's fuel feeding time, the opening of opening and closing core control valve block can ascendingly be opened gradually, overcome the compression shock between system, in protective system, associated components is injury-free, and reduces energy loss; Variable pump systems is at least one second actuator and at least one first actuator's fuel feeding simultaneously, can reduce costs, improve energy-saving effect, can also improve the controllability of system.
In addition, opening and closing core control valve block is controlled by electro-hydraulic control valve block, can input automatically controlled instruction, then be converted into hydraulic control instruction by electro-hydraulic control valve block, and the electrohydraulic integration achieving whole hydraulic system controls, and improves control efficiency.
Accompanying drawing explanation
Accompanying drawing described herein is used to provide further understanding of the present utility model, and form a application's part, schematic description and description of the present utility model, for explaining the utility model, is not formed improper restriction of the present utility model.In the accompanying drawings:
Fig. 1 is the schematic diagram of the utility model automatically controlled opening and closing core hydraulic system.
Fig. 2 is the structural representation of the utility model automatically controlled opening and closing core hydraulic system embodiment.
Fig. 3 is the structural representation of the utility model unloading valve block embodiment.
Fig. 4 is the pressure unloading characteristic curve schematic diagram of the utility model automatically controlled opening and closing core hydraulic system embodiment.
Fig. 5 is the structural representation of another embodiment of the utility model automatically controlled opening and closing core hydraulic system.
In figure: 1-fuel tank, 2-variable displacement pump, 3-commutator, 4-right limit valve, 5-left limit valve, 6-flux amplification valve, 7-left steering oil cylinder, 8-right steering oil cylinder, 9-opening and closing core control valve block, 10-pilot control block, 11-distributing valve, 12-tipping bucket cylinder, 13-swing arm cylinder, 14-electro-hydraulic control valve block, 15-oil return filter cleaner, 16-hydraulic oil radiator, 17-unloading valve block, 18-metering pump, 19-mode of operation diverter switch, 20-electric control handle, 21-controller, 22-pilot-actuated valve, 23-first segment discharge orifice, 24-second one-way valve, 25-relief valve, 26-cartridge valve, 27-second section discharge orifice, 28-the 3rd throttle orifice, 29-first one-way valve, 30-constant difference overflow valve.
Embodiment
Below in conjunction with the accompanying drawing in the utility model embodiment, the technological scheme in embodiment is clearly and completely described.Obviously, described embodiment is only a part of embodiment of the present utility model, instead of whole embodiments.Based on embodiment of the present utility model, those of ordinary skill in the art are not making the every other embodiment obtained under creative work prerequisite, all belong to the scope of the utility model protection.
In description of the present utility model, it will be appreciated that, term " " center ", " transverse direction ", " longitudinal direction ", " front ", " afterwards ", " left side ", " right side ", " on ", D score, " vertically ", " level ", " top ", " end ", " interior ", orientation or the position relationship of the instruction such as " outward " are based on orientation shown in the drawings or position relationship, only the utility model and simplified characterization for convenience of description, instead of indicate or imply that the device of indication or element must have specific orientation, with specific azimuth configuration and operation, therefore the restriction to the utility model protection domain can not be interpreted as.
In order to improve the energy-saving effect of hydraulic system, the utility model first proposed a kind of automatically controlled opening and closing core hydraulic system, the schematic diagram of an one embodiment as shown in Figure 1, composition graphs 2, 3 and 5, this automatically controlled opening and closing core hydraulic system comprises for the Constant Pump System at least one first actuator's fuel feeding, for the variable pump systems at least one second actuator's fuel feeding, opening and closing core control valve block 9 and the electro-hydraulic control valve block 14 be connected with described opening and closing core control valve block 9, the automatically controlled instruction morphing hydraulic control instruction for being used for the openings of sizes controlling described opening and closing core control valve block 9 that described electro-hydraulic control valve block 14 can will receive, described opening and closing core control valve block 9 is connected on the connection oil circuit between described Constant Pump System and described variable pump systems, with the opening and closing by described opening and closing core control valve block 9, make described variable pump systems can simultaneously at least one first actuator described and at least one second actuator's fuel feeding described or be separately at least one second actuator's fuel feeding described.
Above-described embodiment by arranging opening and closing core control valve block between Constant Pump System and variable pump systems, and controlled according to the openings of sizes of automatically controlled instruction to opening and closing core control valve block received by electro-hydraulic control valve block, can make variable pump systems can simultaneously at least one second actuator and at least one first actuator's fuel feeding or be separately at least one second actuator's fuel feeding.Because opening and closing core control valve block can adjust its openings of sizes according to actual needs, therefore when needs variable pump systems be simultaneously at least one second actuator and at least one first actuator's fuel feeding time, the opening of opening and closing core control valve block can ascendingly be opened gradually, overcome the compression shock between system, in protective system, associated components is injury-free, and reduces energy loss; Variable pump systems is at least one second actuator and at least one first actuator's fuel feeding simultaneously, can reduce costs, improve energy-saving effect, can also improve the controllability of system.
In addition, opening and closing core control valve block is controlled by electro-hydraulic control valve block, can input automatically controlled instruction, then be converted into hydraulic control instruction by electro-hydraulic control valve block, and the electrohydraulic integration achieving whole hydraulic system controls, and improves control efficiency.
In the above-described embodiments, the openings of sizes of described opening and closing core control valve block 9 can regulate continuously, belongs to a kind of hydraulic control proportional control valve, and described electro-hydraulic control valve block 14 can control the openings of sizes of described opening and closing core control valve block 9 according to described hydraulic control instruction.Opening and closing core control valve block 9 is made not only to have opening and closing two states like this, the control of variable pump systems to the oil mass of Constant Pump System fuel feeding can also be realized by the control of openings of sizes, and then when also not having enough time comparatively greatly to reduce when the hydraulic fluid pressure in variable pump systems, by the openings of sizes of adjustment opening and closing core control valve block, adjust the hydraulic pressure oil mass entering Constant Pump System.
As shown in Figure 2, in automatically controlled opening and closing core hydraulic system of the present utility model, the automatically controlled instruction that electro-hydraulic control valve block 14 receives can be inputted by automatically controlled or manual handle, then controls opening and closing core control valve block 9.On this basis, controller can also be set up control input instruction.Particularly, automatically controlled opening and closing core hydraulic system also comprises electric control handle 20 and controller 21, described controller 21 can receive the stick control signal that described electric control handle 20 exports, and sends described automatically controlled instruction according to described stick control signal to described electro-hydraulic control valve block 14.
Further, automatically controlled opening and closing core hydraulic system can also comprise the unloading valve block 17 on the working connection being connected to described Constant Pump System, unloading valve block 17 is mainly used in the off-load of Constant Pump System, when needs adopt variable pump systems to carry out fuel feeding at least one first actuator, unloading valve block 17 pairs of Constant Pump System can be adopted to carry out off-load.Inventor is test result experimentally, the actual conditions of incorporation engineering machinery, optimizes principle and the structure of unloading valve block, again mates pressure unloading value and open and shut characteristic, can be described in detail after its concrete structure.
After being provided with unloading valve block 17 in Constant Pump System, when variable pump systems be simultaneously at least one second actuator and at least one first actuator's fuel feeding time, can, by unloading valve block 17 by Constant Pump System off-load, current quantitative and set of variables assembly system be made to switch to entire variable system.Namely entire variable system only has variable pump systems fuel feeding, and it can adjust fuel delivery as required, improves the energy-saving effect of system, overcomes the problem that Constant Pump System energy loss is large, control performance is poor.
The unloading way of unloading valve block 17 has a variety of; such as preset pressure is set in unloading valve block 17; when the induced pressure in Constant Pump System exceedes preset pressure; namely unloading valve block 17 starts unloading function automatically; thus the metering pump in protection Constant Pump System; prevent excess traffic overflow, save engine power.
Its unloading way can also be: described electro-hydraulic control valve block 14 is provided with the hydraulic fluid port P9 be communicated with described unloading valve block 17, described controller 21 can control described electro-hydraulic control valve block 14 and carry out pressure off-load by described unloading valve block 17 to described Constant Pump System, namely operator can be according to actual needs, to controller 21 input control order, make it control electro-hydraulic control valve block 14 the off-load oil circuit of unloading valve block 17 is communicated with, pressure off-load is carried out to Constant Pump System, to meet multiple different demand, such as when low speed super-heavy load shovel dress operating mode or other attached facility supporting, undertaken quantitatively and the switching of set of variables assembly system and entire variable system by forcing off-load, and then energy-conservation and improve controllability.
In order to simplify the operation, automatically controlled opening and closing core hydraulic system can also comprise the mode of operation diverter switch 19 be connected with described controller 21, described controller 21 can receive the output order of described mode of operation diverter switch 19, and controls described electro-hydraulic control valve block 14 according to described output order.That is, if want to carry out pressure off-load to Constant Pump System, operator only need press mode of operation diverter switch 19, simple to operate, and off-load is timely.Will change when operator predict the mode of operation being about to carry out, when adopting normal mode of operation cannot satisfy the demands, can directly press mode of operation diverter switch 19, pressure unloading function can be started, system is made to become entire variable system, to obtain good controllability.
In addition, in order to avoid at least one first actuator move to end of travel time, because the speed of the first actuator is too fast, motional inertia is larger, the enormous impact power of hydraulic oil causes damage to associated components, by programming, relevant early warning program can be set in controller 21 in advance, make described controller 21 can when detecting that at least one first actuator described moves to the end of travel preset length apart from least one the first actuator described, control described electro-hydraulic control valve block 14, by described unloading valve block 17, pressure off-load is carried out to described Constant Pump System, and then reduce the motion speed of the first actuator, reduce and impact.After off-load, entire variable system handling good, can make the first actuator run with speed comparatively stably.In one embodiment, the system-head curve before and after off-load as shown in Figure 4, the pump intake pressure P of metering pump 18 before off-load 1with the pump intake pressure P of variable displacement pump 2 2basically identical, and the pump intake pressure P of metering pump 18 after off-load 1be reduced to 7.6bar, and the pump intake pressure P of variable displacement pump 2 2for 189.9bar, can realize by the conversion to entire variable system of variable and quantita-tive combinations system.
As shown in Figure 3, be the structural representation of the utility model unloading valve block embodiment.This unloading valve block 17 comprises first segment discharge orifice 23, cartridge valve 26 and relief valve 25, the hydraulic fluid port A of described cartridge valve 26 is communicated with the first oil inlet P 5 be arranged on described unloading valve block 17, the hydraulic fluid port B of described cartridge valve 26 is communicated with the oil return inlet T 5 be arranged on described unloading valve block 17, described first segment discharge orifice 23 is connected between described first oil inlet P 5 and the control port X of described cartridge valve 26, between the control port X that described relief valve 25 is arranged at described cartridge valve 26 and described oil return inlet T 5, hydraulic fluid port P9 on described electro-hydraulic control valve block 14 is connected with the control port X of described cartridge valve 26.
With reference to figure 5, when the hydraulic fluid port P9 on electro-hydraulic control valve block 14 is communicated with the control port X of cartridge valve 26, electro-hydraulic control valve block 14 can for the control port X of cartridge valve 26 provide a similar fuel tank without pressure oil port, such as hydraulic fluid port P9 is connected with oil outlet T4, hydraulic fluid port T4 is communicated with fuel tank, the hydraulic oil of being come in by the first oil inlet P 5 on unloading valve block 17 like this will be flowed out by the hydraulic fluid port K on first segment discharge orifice 23 and unloading valve block 17, when having hydraulic oil to flow through in first segment discharge orifice 23, at the two ends of first segment discharge orifice 23 will mineralization pressure poor, namely between the control port X of cartridge valve 26 and hydraulic fluid port A will mineralization pressure poor, the hydraulic oil of the first oil inlet P 5 can make the spool of cartridge valve 26 move upward by hydraulic fluid port A, thus make most hydraulic oil by hydraulic fluid port A by hydraulic fluid port B, and then by oil return inlet T 5 oil sump tank on unloading valve block 17, this process is Constant Pump System carries out forcing off-load overall process by unloading valve block 17.
Preferably, described unloading valve block 17 can also comprise second section discharge orifice 27, between the control port X that described second section discharge orifice 27 is arranged at described cartridge valve 26 and described relief valve 25, for controlling the movement velocity of the spool of described cartridge valve 26, prevent described spool from the opening procedure of control port X, clashing into the valve seat of described cartridge valve 26.This second section discharge orifice 27 mainly plays off-load cushioning and protection.
Preferably, described unloading valve block 17 can also comprise the 3rd throttle orifice 28 and the first one-way valve 29 between hydraulic fluid port A and described first oil inlet P 5 being parallel to described cartridge valve 26, for controlling the movement velocity of the spool of described cartridge valve 26, prevent described spool from the closing process of hydraulic fluid port A, clashing into the valve seat of described cartridge valve 26, and hydraulic oil can be avoided the impact of described first oil inlet P 5 place oil pipe.3rd throttle orifice 28 and the first one-way valve 29 cooperatively interact, the effect of its off-load buffering and protection and anti-back flow jointly.Wherein the 3rd throttle orifice 28 can adopt variable orifice.
If do not arrange second section discharge orifice 27 in unloading valve block 17, 3rd throttle orifice 28 and the first one-way valve 29, oil circuit does not have one-way throttle cushion, then the spool keying speed of cartridge valve 26 is very fast, because the first actuator is in working procedure (such as performing lifting action), oil cylinder internal pressure increases gradually, off-load moment, the flow entering oil cylinder reduces, oil cylinder working-pressure can reduce, this pressure again can lower than the pressure of setting in unloading valve block 17, then cartridge valve 26 is closed again immediately, after closing, the pressure of oil cylinder again can higher than the pressure unloading set up, so start off-load again, appearance like this repeatedly high frequency opens and closes, cause noise and impact.After being provided with second section discharge orifice 27, the 3rd throttle orifice 28 and the first one-way valve 29; buffer protection can be become with control port X-shaped to the hydraulic fluid port A of cartridge valve 26; make the opening and closing of cartridge valve 26 in unloading valve block 17 all comparatively slow; realize the unloading function that unloading valve block 17 is stable; cartridge valve 26 will be caused frequently to open and close because of system pressure fluctuation; thus eliminate system vibration and impact, the working life of extension element and system.
In addition, the second one-way valve 24 can also be set between first oil inlet P 5 and oil outlet P6 of unloading valve block 17, to avoid hydraulic oil to flow back to the first oil inlet P 5 by oil outlet P6, cause the damage to metering pump 18.
In order to prevent spring chamber enclosure portion fluid, cause spool normally cannot move commutation, the spring chamber of relief valve 25 can also directly be connected with oil return inlet T 5.
Unloading valve block 17 is except above-mentioned pressure unloading function, also possesses passive unloading function: oil outlet P6 is communicated with the control chamber of relief valve 25, like this when the pressure of oil outlet P6 is larger, the valve core movement of relief valve 25 can be promoted, the filler opening of relief valve 25 is communicated with oil outlet, the hydraulic oil of the first oil inlet P 5 is namely by first segment discharge orifice 23, then oil return is carried out by relief valve 25, similarly, when having hydraulic oil to flow through in first segment discharge orifice 23, at the two ends of first segment discharge orifice 23 will mineralization pressure poor, namely between the control port X of cartridge valve 26 and hydraulic fluid port A will mineralization pressure poor, the hydraulic oil of the first oil inlet P 5 can make the spool of cartridge valve 26 move upward by hydraulic fluid port A, thus make most hydraulic oil by hydraulic fluid port A by hydraulic fluid port B, and then by oil return inlet T 5 oil sump tank on unloading valve block 17, this process is Constant Pump System carries out passive off-load overall process by unloading valve block 17.
In order to realize the pilot control characteristic of automatically controlled opening and closing core hydraulic system, automatically controlled opening and closing core hydraulic system can also comprise pilot control block 10, described pilot control block 10 can by the variable displacement pump fuel feeding in described variable pump systems, and for described electro-hydraulic control valve block 14 provide pilot control oil, described controller 21 is connected with described pilot control block 10, and controls the break-make of described pilot control block 10 to the oil circuit of described electro-hydraulic control valve block 14 fuel feeding.When pilot control block 10 is to electro-hydraulic control valve block 14 fuel feeding, complete machine can action, once pilot control block 10 blocks to the oil circuit of electro-hydraulic control valve block 14 fuel feeding, the action of complete machine immediately by locking, thus prevents misoperation, improves the Security of complete machine.
In another embodiment, pilot control block 10 also by the metering pump fuel feeding in Constant Pump System, can also provide guide oil by special pioneer pump or accumulator.
Hydraulic oil in electro-hydraulic control valve block 14 can be provided by pilot control block 10, also can be provided by pioneer pump special in addition.When adopting pilot control block 10 to carry out fuel feeding, the break-make of oil feeding line can be controlled by controller 21, such as solenoid directional control valve is set in pilot control block 10, manually or controller 21 change the working position of solenoid directional control valve to control the break-make of described solenoid directional control valve, and then change the on off operating mode of described pilot control block 10 to the oil circuit of described electro-hydraulic control valve block 14 fuel feeding.
Pilot-actuated valve 22 can be comprised in automatically controlled opening and closing core hydraulic system, controlled variable pumps oil mass at any time variable control mechanism pilot control can be carried out for what carry the variable displacement pump in variable pump systems, described pilot-actuated valve 22 can screen load pressure signal larger at least one first actuator described and at least one the second actuator, and feed back to the variable control mechanism of variable displacement pump 2 in described variable pump systems as load feedback signal, and then control the oil pump capacity of described variable displacement pump 2.Pilot-actuated valve 22 screens load pressure signal maximum in all actuators of Constant Pump System and variable pump systems, being to make the fuel delivery of variable displacement pump 2 can meet the demand of all actuators to hydraulic oil, avoiding some actuator cannot complete because being short of power and performing an action.
Preferably; described pilot-actuated valve 22 comprises shuttle valve and the 4th throttle orifice; shuttle valve structure is simple; easy realization; two filler openings of described shuttle valve are respectively used to the load pressure signal receiving at least one first actuator described and at least one the second actuator described; described 4th throttle orifice is between the oil outlet and the outlet of described pilot-actuated valve 22 of described shuttle valve, and for cushioning variable displacement pump 2 and protect, user can change the 4th throttle orifice of different size according to demand.
In order to protect variable displacement pump 2 further; automatically controlled opening and closing core hydraulic system also comprises constant difference overflow valve 30; the filler opening of described constant difference overflow valve 30 is communicated with the oil outlet of described variable displacement pump 2; the oil outlet of described constant difference overflow valve 30 is communicated with fuel tank 1, the spring chamber of described constant difference overflow valve 30 and the outlet of described pilot-actuated valve 22.When the pressure sum of the pressure of the outlet LS2 of pilot-actuated valve 22 and the hydraulic fluid port LS3 of variable displacement pump 2 is less than control chamber pressure (i.e. the oil outlet pressure of variable displacement pump 2) of constant difference overflow valve 30, the valve core movement of constant difference overflow valve 30, the filler opening of constant difference overflow valve 30 is communicated with oil outlet, and the fuel-displaced of variable displacement pump 2 directly flows back to fuel tank by constant difference overflow valve 30.And under normal working, therefore the pressure that the oil outlet pressure of variable displacement pump 2 equals hydraulic fluid port LS3 adds can reduce the setting pressure of the pressure adjusting spring of constant difference overflow valve 30 and the system pressure impact eliminated and produce when opening and closing core control valve 9 opens and closes of doing the best.
When electric control handle 20 returns suddenly meta, opening and closing core control valve block 9 spool is closed rapidly, now variable displacement pump 2 discharge capacity does not have enough time to reduce, but due to the stopping of at least one the first actuator action, the pressure of the outlet LS2 of pilot-actuated valve 22 reduces, and therefore the spring chamber pressure of constant difference overflow valve 30 reduces rapidly, and the pressure of variable displacement pump 2 pumping hole is set up by constant difference overflow valve 30, hydraulic oil overflows back fuel tank through the return opening of constant difference overflow valve 30, makes greatly to reduce the surge pressure of variable displacement pump 2.
In the embodiment of above-mentioned each illustrated automatically controlled opening and closing core hydraulic system, at least one first actuator can be Operation System, such as tipping bucket cylinder, swing arm cylinder etc., at least one second actuator can be non-Operation System, such as turn to, certainly be also not limited thereto, its specific constructive form can have multiple choices, automatically controlled opening and closing core hydraulic system is applied to different engineering machinery, and at least one first actuator and at least one second actuator correspond to different mechanical parts.
In a preferred embodiment, at least one first actuator described comprises tipping bucket cylinder 12 and swing arm cylinder 13, distributing valve 11 is provided with in described Constant Pump System, described electro-hydraulic control valve block 14 is provided with the hydraulic fluid port that at least one valve core movement for described distributing valve 11 provides pilot control oil, described distributing valve 11, for controlling the action of described tipping bucket cylinder 12 and described swing arm cylinder 13, described distributing valve 11 is provided with the hydraulic fluid port P3 be connected with described opening and closing core control valve block 9.
As shown in Figure 5, electro-hydraulic control valve block 14 is provided with four for controlling the hydraulic fluid port of distributing valve 11, be respectively a1, a2, b1 and b2, connect hydraulic fluid port A1, A2, B1 and B2 of distributing valve 11 respectively, for controlling the working position of changeover valve core in distributing valve 11, and then control the different actions of tipping bucket cylinder 12 and swing arm cylinder 13.In addition, electro-hydraulic control valve block 14 is also provided with hydraulic fluid port 2c, is connected with the hydraulic fluid port 2C on distributing valve 11, to deallocate the locking effect of valve 11 inner equilibrium valve to tipping bucket cylinder 12 or swing arm cylinder 13.
With reference in the preferred embodiment shown in figure 5, the working procedure of Constant Pump System is specially:
Under normal working, the fuel-displaced direct supply distributing valve 11 of metering pump 18, under the pilot control of electro-hydraulic control valve block 14, two three six-way transfer valves in distributing valve 11 are in different working positions respectively, when the first selector valve being positioned at below (below as shown in Figure 5) is in left position, hydraulic oil on working connection enters the rod chamber of tipping bucket cylinder 12, and the piston rod of tipping bucket cylinder 12 is retracted, tipping bucket discharging; When the first selector valve is in right position, the hydraulic oil on working connection enters the rodless cavity of tipping bucket cylinder 12, and the piston rod of tipping bucket cylinder 12 stretches out, and performs and receives bucket action; When the first selector valve is in meta, hydraulic oil on working connection directly reaches the second selector valve being positioned at top (top as shown in Figure 5) by the first selector valve, under the pilot control of electro-hydraulic control valve block 14, when the second selector valve is in left position, hydraulic oil on working connection enters the rod chamber of swing arm cylinder 13, the piston rod of swing arm cylinder 13 is retracted, and swing arm is retracted; When the second selector valve is in right position, the hydraulic oil on working connection enters the rodless cavity of swing arm cylinder 13, and the piston rod of swing arm cylinder 13 stretches out, and performs swing arm extend action; When the second selector valve is in meta, the hydraulic oil on working connection directly flows back to fuel tank 1.
In addition, be also provided with multiple equilibrium valve in distributing valve 11, the structural type of equilibrium valve also can have multiple, and Pilot operated check valve such as can be adopted to use as equilibrium valve, and common one-way valve and relief valve also can be adopted to combine as equilibrium valve etc.The effect of equilibrium valve mainly prevents tipping bucket cylinder 12 and swing arm cylinder 13 oil return rapidly under emergency situations, causes oil cylinder to damage, plays balance, protection and locking effect.Certainly, being also provided with the parts for removing locking in distributing valve 11, the locking effect of valve 11 inner equilibrium valve to tipping bucket cylinder 12 or swing arm cylinder 13 can being deallocated by the hydraulic fluid port 2c on electro-hydraulic control valve block 14.
In another preferred embodiment, at least one second actuator described comprises left steering oil cylinder 7 and right steering oil cylinder 8, commutator 3 and flux amplification valve 6 is provided with in described variable pump systems, described commutator 3 is for controlling described flux amplification valve 6, and the action of described left steering oil cylinder 7 and described right steering oil cylinder 8 is controlled by described flux amplification valve 6, described flux amplification valve 6 is provided with the hydraulic fluid port EF be connected with described opening and closing core control valve block 9.
As shown in Figure 5, the hydraulic fluid port XZ of pilot control block 10 is connected with the oil inlet P of commutator 3, i.e. the pilot control oil of commutator 3 can be provided by pilot control block 10, and special pioneer pump or accumulator can certainly be adopted to carry out fuel feeding.
The right oil outlet R of commutator 3 is connected with right limit valve 4 and left limit valve 5 respectively with left oil outlet L, is respectively used to the break-make of oil circuit control R1 and oil circuit L1.Oil circuit R1 and oil circuit L1 is connected to the selector valve in flux amplification valve 6, for controlling the action of left steering oil cylinder 7 and right steering oil cylinder 8.
In addition, being also provided with pressure-gradient control valve in flux amplification valve 6, is the fuel delivery of Constant Pump System fuel feeding for controlled variable pumping system together with opening and closing core control valve block 9.Such as, when opening and closing core control valve block 9 is opened, pressure-gradient control valve is in different working positions, and variable pump systems is that the oil mass of Constant Pump System fuel feeding is different; When opening and closing core control valve block 9 closes, no matter which working position pressure-gradient control valve is in, variable pump systems all not specified rate pumping system fuel feeding.
Also be provided with shuttle valve in flux amplification valve 6, the outlet of shuttle valve is connected with the hydraulic fluid port LS1 of pilot-actuated valve 22, for screening load pressure signal larger between left steering oil cylinder 7 and right steering oil cylinder 8, and is fed back to pilot-actuated valve 22.
With reference in the preferred embodiment shown in figure 5, the working procedure of variable pump systems is specially:
Variable displacement pump 2 go out oil content two-way, one road supply flow amplifying valve 6, one tunnel supply pilot control block 10, the guide oil of pilot control block 10 can control commutator 3, after the hydraulic oil that pilot control block 10 takes from variable displacement pump 2 enters commutator 3, when manipulator handle commutator 3 turn left time, the hydraulic fluid port L of commutator 3 is communicated with oil inlet P, hydraulic fluid port R is communicated with oil outlet T, hydraulic oil can enter left limit valve 5 through hydraulic fluid port L, the fluid entering left limit valve 5 enters the right position control chamber of the selector valve in flux amplification valve 6 through oil circuit L1, hydraulic oil promotes selector valve and is moved to the left, simultaneously owing to selector valve being also provided with the path that hydraulic oil can be made from right control chamber bit stream control chamber position left, hydraulic oil can be made by oil circuit R1, hydraulic fluid port R and the oil outlet T of right limit valve 4 and commutator flow back to, this path is also provided with throttle orifice, this throttle orifice makes mineralization pressure between the left control chamber of selector valve and right control chamber poor, this pressure difference can help change-over valve core to be moved to the left fast, and then realize fast steering,
Similarly, when manipulator handle commutator 3 turn right time, the hydraulic fluid port R of commutator 3 is communicated with oil inlet P, hydraulic fluid port L is communicated with oil outlet T, hydraulic oil can enter right limit valve 4 through hydraulic fluid port R, the fluid entering right limit valve 4 enters the left control chamber of the selector valve in flux amplification valve 6 through oil circuit R1, hydraulic oil promotes selector valve and moves right, hydraulic oil can be made to flow to the path of right control chamber from left control chamber due to selector valve being also provided with simultaneously, hydraulic oil can be made quickly through oil circuit L1, hydraulic fluid port L and the oil outlet T of left limit valve 5 and commutator flow back to, this path is also provided with throttle orifice, this throttle orifice makes mineralization pressure between the left control chamber of selector valve and right control chamber poor, this pressure difference can help change-over valve core to move right fast, and then realize fast steering.
Particularly, when the right position of selector valve is in working position, the fluid on variable pump systems working connection enters the rodless cavity of right steering oil cylinder 8 and the rod chamber of left steering oil cylinder 7, and the piston rod of right steering oil cylinder 8 is stretched out, simultaneously the piston rod of left steering oil cylinder 7 is retracted, complete machine turn left to; When the left position of selector valve is in working position, fluid on variable pump systems working connection enters the rodless cavity of left steering oil cylinder 7 and the rod chamber of right steering oil cylinder 8, the piston rod of left steering oil cylinder 7 is stretched out, and simultaneously the piston rod of right steering oil cylinder 8 is retracted, complete machine turn right to.
In hydraulic oil on variable pump systems working connection and the second actuator, larger induced pressure can also control the valve core movement of the pressure-gradient control valve in flux amplification valve 6, pressure-gradient control valve is made to be in different working positions, the number being Constant Pump System fuel feeding with controlled variable pumping system.
In Figure 5, the oil return circuit of described Constant Pump System can also be disposed with the hydraulic oil radiator 16 for dispelling the heat to hydraulic oil and the oil return filter cleaner 15 for filtering hydraulic oil.Wherein the filler opening of hydraulic oil radiator 16 is connected with the oil return inlet T 3 of distributing valve 11, for dispelling the heat to the working oil oil return at least one first actuator, in order to avoid high oil temperature causes the adverse effect to fuel tank, and original hydraulic oil in fuel tank is avoided to heat up.In order to avoid the hydraulic oil in fuel tank is polluted in working oil oil return, be provided with oil return filter cleaner 15 between the oil outlet of hydraulic oil radiator 16 and fuel tank, to carry out filtration scrubbing to oil return.
The oil return inlet T 5 of described unloading valve block 17 is connected between the outlet of described hydraulic oil radiator 16 and the filler opening of described oil return filter cleaner 15, be oil sump tank after making the oil return of unloading valve block 17 directly be filtered by oil return filter cleaner 15 like this, and without hydraulic oil radiator 16, compared with the impact of large discharge to hydraulic oil radiator 16 when can avoid 17 off-load of unloading valve block.
Certainly, the various embodiments described above are only preferred versions of the present utility model, are specifically not limited thereto, and can make pointed adjustment according to actual needs on this basis, thus obtain different embodiments.Such as, the control mode of variable displacement pump 2 changes to automatically controlled by the basis of above-described embodiment, or the control mode of opening and closing core control valve block 9 is also changed into automatically controlled etc.Because mode in the cards is more, just illustrate no longer one by one here.
Based on above-mentioned automatically controlled opening and closing core hydraulic system, the utility model also proposes a kind of engineering machinery, comprises the automatically controlled opening and closing core hydraulic system in the various embodiments described above.
In order to the technological scheme making those skilled in the art understand each embodiment of the utility model better, below in conjunction with an embodiment of automatically controlled opening and closing core hydraulic system as shown in Figure 5, further illustrate the function that can realize in this system:
1, the realization of opening and closing core working method:
When in the process of complete machine at straight line moving, because steering system (left steering oil cylinder 7 and right steering oil cylinder 8) and work system (tipping bucket cylinder 12 and swing arm cylinder 13) are all without feedback signal, the LS2 hydraulic fluid port no signal of pilot-actuated valve 22 exports, variable displacement pump 2 is standby, and now opening and closing core control valve 9 is in and closes wick-like state; When in complete machine running process, when system only turns to, because distributing valve 11 is for leaving core, the pressure drop that the flow of metering pump 18 is formed by its meta is very little, is not enough to open opening and closing core control valve block 9, so, now opening and closing core control valve 9 is still in and closes wick-like state, energy saving of system successful; When work system (tipping bucket cylinder 12 and swing arm cylinder 13) action, the hydraulic oil demand of distributing valve 11 improves, controller 21 sends control signal to electro-hydraulic control valve block 14, opening and closing core control valve block 9 is controlled by the annexation between the hydraulic fluid port P10 of electro-hydraulic control valve block 14 and the hydraulic fluid port n of opening and closing core control valve block 9, make it be in out wick-like state, namely the hydraulic oil of variable pump systems flow to Constant Pump System by opening and closing core control valve block 9.When work system (tipping bucket cylinder 12 and swing arm cylinder 13) stops action, the spool that electro-hydraulic control valve block 14 controls opening and closing core control valve block 9 is again got back to and is closed core position, reduces the loss of variable displacement pump 2.
2, switching working mode:
Under normal mode of operation, mode of operation diverter switch 19 must not be electric, and unloading valve block 17 is in normal working, and the second control chamber fluid of cartridge valve 26 can not communicate with oil return, and whether off-load is determined by the pressure of P6 hydraulic fluid port unloading valve block 17.After pressing mode of operation diverter switch 19, mode of operation diverter switch 19 obtains electric, export control signal to controller 21 simultaneously, after via controller 21 processes, control signal is exported to electro-hydraulic control valve block 14 by controller 21, the control command that electro-hydraulic control valve block 14 implementation controller 21 exports, can control unloading valve block 17 and carry out pressure off-load.
Specifically, when pressing mode of operation diverter switch 19, hydraulic fluid port P9 on electro-hydraulic control valve block 14 is communicated with the oil return inlet T 5 on unloading valve block 17, second control chamber fluid of cartridge valve 26 is through hydraulic fluid port K oil return, and first segment discharge orifice 23 has fluid to flow, and the spool two ends of cartridge valve 26 form pressure reduction, spool is opened, unloading valve block 17 is in pressure unloading condition, the direct off-load oil sump tank of hydraulic oil of metering pump 18, and quantitative and set of variables assembly system is switched to entire variable system.Now, the movement speed of work system (tipping bucket cylinder 12 and swing arm cylinder 13) can be slack-off, but work system (tipping bucket cylinder 12 and swing arm cylinder 13), steering system (left steering oil cylinder 7 and right steering oil cylinder 8) are variable system, there is good maneuverability and micro-control, and energy-saving effect is comparatively quantitative and set of variables assembly system is more obvious, this kind of mode of operation is applicable to low speed super-heavy load shovel dress operating mode, or other subsidiary body supporting, all has good control performance.
3, off-load buffering and protection:
In work system (tipping bucket cylinder 12 and swing arm cylinder 13) course of action (such as spading process); the P6 hydraulic fluid port pressure of unloading valve block 17 raises; after reaching setting pressure, unloading valve block 17 starts off-load; thus protection metering pump 18; prevent excess traffic overflow, save engine power.Now, the high pressure of work system (tipping bucket cylinder 12 and swing arm cylinder 13) is born by variable displacement pump 2, when system pressure raises further, when reaching variable displacement pump 2 cut-out pressure, variable displacement pump 2 discharge capacity automatically return be discharged to minimum, eliminate spill losses.
Specific implementation process is as follows: when P6 hydraulic fluid port pressure reaches setting pressure, relief valve 25 is opened, and the segment fluid flow of P5 hydraulic fluid port, through first segment discharge orifice 23, then flow to T5 mouth through relief valve 25; The fluid flowing through first segment discharge orifice 23 is poor at restriction two ends mineralization pressure, this pressure difference acts on the second control chamber and the spring chamber of cartridge valve 26, the spool of cartridge valve 26 is opened, in opening process, second section discharge orifice 27 can slow down spool opening speed, prevent spool from clashing into valve seat, extend the spool life-span.When P6 hydraulic fluid port pressure is lower than setting pressure, relief valve 25 cuts out, flow through the flow vanishing of first segment discharge orifice 23, pressure at two ends difference reduces to zero, the spool of cartridge valve 26 resets under spring force, now due to the acting in conjunction of the 3rd throttle orifice 28 and the first one-way valve 29, speed that spool closes can be slowed down thus avoid the compression shock that spool quick closedown causes.In addition, P6 mouth high pressure oil and P5 mouth low pressure oil are kept apart by the second one-way valve 24, can protect metering pump 18.
4, lifting process end buffering and protection:
By adjusting the preset pressure of relief valve 25, when the pressure in work system (tipping bucket cylinder 12 and swing arm cylinder 13) is greater than setting value (gross weight that such as user shovels dress material exceedes setting value), a bit of stroke L0 can be reserved at the end of boom cylinder 13 lifting stroke, opening and closing core control valve block 9 is opened in this trip L0, variable pump systems can be made to be tipping bucket cylinder 12 and swing arm cylinder 13 fuel feeding, at the end of lifting process, only has variable displacement pump 2 fuel feeding, lifting speed can be reduced, the compression shock of boom cylinder 13 inside when reducing to give rise to top, complete machine work is more steady, safety.System unloaded pressure diagram after optimization as shown in Figure 4.
5, pilot control electric controlled safety lock is only:
Accessible site solenoid directional control valve in pilot control block, when solenoid directional control valve obtains electric, the P4 hydraulic fluid port of electro-hydraulic control valve block 14 has pressure oil to export, complete machine can action, once complete machine power-off or stopping are energized to solenoid directional control valve, the action of complete machine immediately by locking, thus prevents misoperation, improves the Security of complete machine.
6, variable displacement pump oil outlet compression shock is eliminated:
When not increasing constant difference overflow valve 30, when electric control handle 20 returns suddenly meta, the oil circuit controlling distributing valve 11 in the electro-hydraulic control valve block 14 that controller 21 controls disconnects, distributing valve 11 times metas, the action of work system (tipping bucket cylinder 12 and swing arm cylinder 13) stops, simultaneously due to hydraulic fluid port P10 and the hydraulic fluid port a1 controlling work system (tipping bucket cylinder 12 and swing arm cylinder 13) of electro-hydraulic control valve block 14, a2, b1, interaction relation between b2, the spool of opening and closing core control valve block 9 is closed rapidly, now the discharge capacity of variable displacement pump 2 does not have enough time to reduce, pumping hole is caused to occur high compression shock, this surge pressure exceedes the cut-out pressure of variable displacement pump 2, cause variable displacement pump 2 row of going back to rapidly, cause the damage to variable displacement pump 2.
After increasing constant difference overflow valve 30, when electric control handle 20 returns suddenly meta, opening and closing core control valve block 9 spool is closed rapidly, now variable displacement pump 2 discharge capacity does not have enough time to reduce, but due to the stopping of work system (tipping bucket cylinder 12 and swing arm cylinder 13) action, the pressure of the outlet LS2 of pilot-actuated valve 22 reduces, therefore the spring chamber pressure of constant difference overflow valve 30 reduces rapidly, the pressure of variable displacement pump 2 pumping hole is set up by constant difference overflow valve 30, hydraulic oil overflows back fuel tank through the return opening of constant difference overflow valve 30, makes greatly to reduce the surge pressure of variable displacement pump 2.
By the explanation of the multiple embodiments to the utility model automatically controlled opening and closing core hydraulic system and engineering machinery, can see that the utility model automatically controlled opening and closing core hydraulic system and engineering machinery are implemented example and at least had one or more advantages following:
(1) by mode of operation diverter switch, unloading valve block and the electro-hydraulic control valve block realizing the switching of opening and closing core system intelligence, quantitative and set of variables assembly system directly can be switched to entire variable system, improve energy-saving effect and the micro-control of hydraulic system, be particularly useful for low speed extra-heavy duty.When switching to entire variable system, complete machine has fabulous expansion, can carry out work by supporting multiple attached facility.
(2) integrated valve block can be adopted for unloading valve block, electro-hydraulic control valve block, pilot control block etc., reduce pipeline and connect, simplify system.
(3) realize stable unloading function by unloading valve block, unloading valve block will be caused frequently to open and close because of system pressure fluctuation, thus eliminate system vibration and impact, the working life of extension element and system.
(4) adopt pilot control block to provide pilot control for commutator and electro-hydraulic control valve block, the structure such as pioneer pump and relief valve can be omitted, simplify system, and eliminate the energy loss of relief valve.
(5) system adopts the commutator of small displacement to be used as the hydraulic pilot level of flux amplification valve, thus the restriction loss of coaxial flow amplifying steering unit inside when eliminating fast steering, reduce fuel consume;
(6) oil return of unloading valve block directly takes back hydraulic oil container, without hydraulic oil radiator, and Oil shocking hydraulic oil radiator when can prevent unexpected off-load.
(7) integrated solenoid directional control valve in pilot control block, the pilot control of work system can adopt solenoid directional control valve locking, safe and efficient.
(8) variable displacement pump pumping hole adopts constant difference overflow valve, eliminates pump intake pressure and impacts, greatly extend the working life of variable displacement pump.
Finally should be noted that: above embodiment is only in order to illustrate that the technical solution of the utility model is not intended to limit; Although be described in detail the utility model with reference to preferred embodiment, those of ordinary skill in the field have been to be understood that: still can modify to embodiment of the present utility model or carry out equivalent replacement to portion of techniques feature; And not departing from the spirit of technical solutions of the utility model, it all should be encompassed in the middle of the technological scheme scope of the utility model request protection.

Claims (17)

1. an automatically controlled opening and closing core hydraulic system, it is characterized in that, comprise for the Constant Pump System at least one first actuator's fuel feeding, for the variable pump systems at least one second actuator's fuel feeding, opening and closing core control valve block (9) and the electro-hydraulic control valve block (14) be connected with described opening and closing core control valve block (9), the automatically controlled instruction morphing hydraulic control instruction for being used for the openings of sizes controlling described opening and closing core control valve block (9) that described electro-hydraulic control valve block (14) can will receive, described opening and closing core control valve block (9) is connected on the connection oil circuit between described Constant Pump System and described variable pump systems, with the opening and closing by described opening and closing core control valve block (9), make described variable pump systems can simultaneously at least one first actuator described and at least one second actuator's fuel feeding described or be separately at least one second actuator's fuel feeding described.
2. automatically controlled opening and closing core hydraulic system according to claim 1 and 2, it is characterized in that, also comprise electric control handle (20) and controller (21), described controller (21) can receive the stick control signal that described electric control handle (20) exports, and sends described automatically controlled instruction according to described stick control signal to described electro-hydraulic control valve block (14).
3. automatically controlled opening and closing core hydraulic system according to claim 2, it is characterized in that, also comprise the unloading valve block (17) on the working connection being connected to described Constant Pump System, described electro-hydraulic control valve block (14) is provided with the hydraulic fluid port P9 be communicated with described unloading valve block (17), described controller (21) can control described electro-hydraulic control valve block (14) and carry out pressure off-load by described unloading valve block (17) to described Constant Pump System.
4. automatically controlled opening and closing core hydraulic system according to claim 3, it is characterized in that, also comprise the mode of operation diverter switch (19) be connected with described controller (21), described controller (21) can receive the output order of described mode of operation diverter switch (19), and controls described electro-hydraulic control valve block (14) according to described output order.
5. automatically controlled opening and closing core hydraulic system according to claim 4, it is characterized in that, described controller (21) when detecting that at least one first actuator described moves to the end of travel preset length apart from least one the first actuator described, can control described electro-hydraulic control valve block (14) and carrying out pressure off-load by described unloading valve block (17) to described Constant Pump System.
6. automatically controlled opening and closing core hydraulic system according to claim 3, it is characterized in that, described unloading valve block (17) comprises first segment discharge orifice (23), cartridge valve (26) and relief valve (25), the hydraulic fluid port A of described cartridge valve (26) is communicated with the first oil inlet P 5 be arranged on described unloading valve block (17), the hydraulic fluid port B of described cartridge valve (26) is communicated with the oil return inlet T 5 be arranged on described unloading valve block (17), described first segment discharge orifice (23) is connected between the control port X of described first oil inlet P 5 and described cartridge valve (26), between the control port X that described relief valve (25) is arranged at described cartridge valve (26) and described oil return inlet T 5, hydraulic fluid port P9 on described electro-hydraulic control valve block (14) is connected with the control port X of described cartridge valve (26).
7. automatically controlled opening and closing core hydraulic system according to claim 6, it is characterized in that, described unloading valve block (17) also comprises second section discharge orifice (27), described second section discharge orifice (27) is arranged between the control port X of described cartridge valve (26) and described relief valve (25), for controlling the movement velocity of the spool of described cartridge valve (26), prevent described spool from the opening procedure of control port X, clashing into the valve seat of described cartridge valve (26).
8. automatically controlled opening and closing core hydraulic system according to claim 6, it is characterized in that, described unloading valve block (17) also comprises the 3rd throttle orifice (28) between hydraulic fluid port A and described first oil inlet P 5 and the first one-way valve (29) that are parallel to described cartridge valve (26), for controlling the movement velocity of the spool of described cartridge valve (26), prevent described spool from the closing process of hydraulic fluid port A, clashing into the valve seat of described cartridge valve (26), and hydraulic oil can be avoided the impact of described first oil inlet P 5 place oil pipe.
9. automatically controlled opening and closing core hydraulic system according to claim 2, it is characterized in that, also comprise pilot control block (10), described pilot control block (10) is by the variable displacement pump fuel feeding in described variable pump systems, and be that described electro-hydraulic control valve block (14) provides pilot control oil, described controller (21) is connected with described pilot control block (10), and controls the break-make of described pilot control block (10) to the oil circuit of described electro-hydraulic control valve block (14) fuel feeding.
10. automatically controlled opening and closing core hydraulic system according to claim 9, it is characterized in that, be provided with solenoid directional control valve in described pilot control block (10), described controller (21) controls the break-make of described pilot control block (10) to the oil circuit of described electro-hydraulic control valve block (14) fuel feeding by the break-make controlling described solenoid directional control valve.
11. automatically controlled opening and closing core hydraulic systems according to claim 2, it is characterized in that, also comprise pilot-actuated valve (22), described pilot-actuated valve (22) is for screening load pressure signal larger at least one first actuator described and at least one second actuator described, and feed back to the variable control mechanism of variable displacement pump (2) in described variable pump systems as load feedback signal, and then control the oil pump capacity of described variable displacement pump (2).
12. automatically controlled opening and closing core hydraulic systems according to claim 11, it is characterized in that, described pilot-actuated valve (22) comprises shuttle valve and the 4th throttle orifice, two filler openings of described shuttle valve are respectively used to the load pressure signal receiving at least one first actuator described and at least one the second actuator described, and described 4th throttle orifice is positioned between the oil outlet of described shuttle valve and the outlet of described pilot-actuated valve (22).
13. automatically controlled opening and closing core hydraulic systems according to claim 11 or 12, it is characterized in that, also comprise constant difference overflow valve (30), the filler opening of described constant difference overflow valve (30) is communicated with the oil outlet of described variable displacement pump (2), the oil outlet of described constant difference overflow valve (30) is communicated with fuel tank (1), the spring chamber of described constant difference overflow valve (30) and the outlet of described pilot-actuated valve (22).
14. automatically controlled opening and closing core hydraulic systems according to claim 1, it is characterized in that, at least one first actuator described comprises tipping bucket cylinder (12) and swing arm cylinder (13), distributing valve (11) is provided with in described Constant Pump System, described electro-hydraulic control valve block (14) is provided with the hydraulic fluid port that at least one valve core movement being described distributing valve (11) provides pilot control oil, described distributing valve (11) is for controlling the action of described tipping bucket cylinder (12) and described swing arm cylinder (13), described distributing valve (11) is provided with the hydraulic fluid port P3 be connected with described opening and closing core control valve block (9).
15. automatically controlled opening and closing core hydraulic systems according to claim 1, it is characterized in that, at least one second actuator described comprises left steering oil cylinder (7) and right steering oil cylinder (8), commutator (3) and flux amplification valve (6) is provided with in described variable pump systems, described commutator (3) is for controlling described flux amplification valve (6), and the action of described left steering oil cylinder (7) and described right steering oil cylinder (8) is controlled by described flux amplification valve (6), described flux amplification valve (6) is provided with the hydraulic fluid port EF be connected with described opening and closing core control valve block (9).
16. automatically controlled opening and closing core hydraulic systems according to claim 3, it is characterized in that, the oil return circuit of described Constant Pump System is disposed with the hydraulic oil radiator (16) for dispelling the heat to hydraulic oil and the oil return filter cleaner (15) for filtering hydraulic oil, the oil return inlet T 5 of described unloading valve block (17) is connected between the outlet of described hydraulic oil radiator (16) and the filler opening of described oil return filter cleaner (15).
17. 1 kinds of engineering machinery, is characterized in that, comprise the automatically controlled opening and closing core hydraulic system as described in any one of claim 1 ~ 16.
CN201520653048.2U 2015-08-26 2015-08-26 Automatically controlled switching core hydraulic system and engineering machinery Withdrawn - After Issue CN204985186U (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201520653048.2U CN204985186U (en) 2015-08-26 2015-08-26 Automatically controlled switching core hydraulic system and engineering machinery

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201520653048.2U CN204985186U (en) 2015-08-26 2015-08-26 Automatically controlled switching core hydraulic system and engineering machinery

Publications (1)

Publication Number Publication Date
CN204985186U true CN204985186U (en) 2016-01-20

Family

ID=55119559

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201520653048.2U Withdrawn - After Issue CN204985186U (en) 2015-08-26 2015-08-26 Automatically controlled switching core hydraulic system and engineering machinery

Country Status (1)

Country Link
CN (1) CN204985186U (en)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105134695A (en) * 2015-08-26 2015-12-09 徐工集团工程机械股份有限公司科技分公司 Electric control opening and closing core hydraulic system and engineering machine
CN105822613A (en) * 2016-05-27 2016-08-03 徐工集团工程机械股份有限公司科技分公司 Integrated valve block based on load feedback control and system based on load feedback control
CN106224306A (en) * 2016-09-29 2016-12-14 徐工集团工程机械股份有限公司科技分公司 There is the hydraulic system of flow-compensated function
CN106499682A (en) * 2016-12-27 2017-03-15 中交第二航务工程局有限公司 A kind of hydraulic system for pile driving barge
WO2017219338A1 (en) * 2016-06-24 2017-12-28 邵正国 Hydraulic system of hydraulic machine for solid waste from sewage
CN109268331A (en) * 2018-11-09 2019-01-25 中国船舶重工集团公司第七〇九研究所 A kind of combination counterbalance valve and back pressure apparatus
CN110645234A (en) * 2019-08-23 2020-01-03 江苏高德液压机械有限公司 Control method of hydraulic system of three-direction shearing and packaging machine
CN113757203A (en) * 2021-09-13 2021-12-07 徐工集团工程机械股份有限公司科技分公司 Loader electric control hydraulic system and loader
CN115584772A (en) * 2022-12-13 2023-01-10 徐工集团工程机械股份有限公司科技分公司 Energy-saving hydraulic system of electric loader and electric loader

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105134695A (en) * 2015-08-26 2015-12-09 徐工集团工程机械股份有限公司科技分公司 Electric control opening and closing core hydraulic system and engineering machine
CN105822613A (en) * 2016-05-27 2016-08-03 徐工集团工程机械股份有限公司科技分公司 Integrated valve block based on load feedback control and system based on load feedback control
WO2017219338A1 (en) * 2016-06-24 2017-12-28 邵正国 Hydraulic system of hydraulic machine for solid waste from sewage
CN106224306A (en) * 2016-09-29 2016-12-14 徐工集团工程机械股份有限公司科技分公司 There is the hydraulic system of flow-compensated function
CN106224306B (en) * 2016-09-29 2019-03-15 徐工集团工程机械股份有限公司科技分公司 Hydraulic system with flow-compensated function
CN106499682A (en) * 2016-12-27 2017-03-15 中交第二航务工程局有限公司 A kind of hydraulic system for pile driving barge
CN106499682B (en) * 2016-12-27 2018-07-06 中交第二航务工程局有限公司 A kind of hydraulic system for pile driving barge
CN109268331A (en) * 2018-11-09 2019-01-25 中国船舶重工集团公司第七〇九研究所 A kind of combination counterbalance valve and back pressure apparatus
CN110645234A (en) * 2019-08-23 2020-01-03 江苏高德液压机械有限公司 Control method of hydraulic system of three-direction shearing and packaging machine
CN113757203A (en) * 2021-09-13 2021-12-07 徐工集团工程机械股份有限公司科技分公司 Loader electric control hydraulic system and loader
CN113757203B (en) * 2021-09-13 2022-04-15 徐工集团工程机械股份有限公司科技分公司 Loader electric control hydraulic system and loader
CN115584772A (en) * 2022-12-13 2023-01-10 徐工集团工程机械股份有限公司科技分公司 Energy-saving hydraulic system of electric loader and electric loader

Similar Documents

Publication Publication Date Title
CN204985186U (en) Automatically controlled switching core hydraulic system and engineering machinery
CN105134695A (en) Electric control opening and closing core hydraulic system and engineering machine
CN204985136U (en) Unloading valve piece, switching core hydraulic system and engineering machinery
JP5574375B2 (en) Energy regeneration control circuit and work machine
CN105090154B (en) A kind of unloading valve block, opening and closing core hydraulic system and engineering machinery
CN106759621B (en) Load-sensitive formula loading machine determines variable delivery hydraulic system
CN104929183B (en) A kind of loader turned to based on Flow amplification determines variable delivery hydraulic system
CN205742337U (en) A kind of hydraulic crawler excavator fluid Regeneration control loop
CN104520594B (en) There is the system without metering hydraulic of power modulation
JP6453711B2 (en) Pressure oil recovery system for work machines
CN105156391A (en) Composite variable pump and hydraulic control system using composite variable pump
CN103807232B (en) The fluid pressure drive device of engineering machinery
CN204849889U (en) Variable hydraulic system is decided to loader based on flow is enlarged to be turned to
CN107489663B (en) A kind of variable pump and the hydraulic control system with variable pump
CN107489664B (en) A kind of load-sensitive and volumetric void fraction formula variable pump and electrohydraulic control system
CN107542729B (en) A kind of complex controll formula hydraulic pump and composite hydraulic control system
CN105134678A (en) Pilot control valve block, core opening and closing hydraulic system and engineering machine
CN202851491U (en) Load-sensitive multi-way valve used in loader variable system
CN212672126U (en) High-altitude operation vehicle and full-floating control system of walking chassis thereof
CN103132557B (en) Excavator and priority control loop of excavator
CN104912137A (en) Excavator hydraulic system with energy feedback function
CN113494111B (en) Main control valve, fixed variable hydraulic system and loader
CN213744202U (en) Control system of hydraulic cylinder and excavator
CN109210024A (en) Minus flow hydraulic control oil circuit and hydraulic system and excavator
CN208346895U (en) Loading machine stable module system

Legal Events

Date Code Title Description
C14 Grant of patent or utility model
GR01 Patent grant
AV01 Patent right actively abandoned

Granted publication date: 20160120

Effective date of abandoning: 20171003

AV01 Patent right actively abandoned