CN205401282U - Breaker hydraulic control system - Google Patents
Breaker hydraulic control system Download PDFInfo
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- CN205401282U CN205401282U CN201620146332.5U CN201620146332U CN205401282U CN 205401282 U CN205401282 U CN 205401282U CN 201620146332 U CN201620146332 U CN 201620146332U CN 205401282 U CN205401282 U CN 205401282U
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Abstract
The utility model discloses a breaker hydraulic control system, including two pneumatic cylinders, magenetic exchange valve, ball valve, bi -pass governing valve, proportion pressure flow compound control valve, pressure relay, forced air cooler, travel switch, pressure sensor and displacement sensor. The piston rod of pneumatic cylinder according to the speed operation of setting for, carries out the breakage to the material under the control of each solenoid valve and governing valve. This breaker hydraulic system can guarantee the jump bit can not the mutual interference and running frequency can adjust, the system can accomplish the reciprocal broken work of assaulting voluntarily. Meetting the system pressure that automatic to rise under the hard material condition, carry out attrition crushing, improvement crushing efficiency to the material. And this system utilizes the normal work of limited control valve furthest's assurance system to make components and parts be in intermittent type operating condition, improve the operational reliability, when partial components and parts break down, can change under the circumstances of not shutting down, improved the work efficiency of breaker.
Description
Technical field
This utility model relates to a kind of crusher control system, particularly relates to a kind of crusher hydraulic and controls system.
Background technology
Along with rapid development of economy, the industry such as highway, high ferro, water conservancy, chemical industry, cement are also flourish therewith, and the development of these industries be unable to do without the raw materials such as some necessary Ores, and these raw materials are general all relatively larger, it is unsuitable for direct application, these raw materials or reclaiming waste material need to be carried out broken processing and process, to carry out corresponding production and construction and processing.Work efficiency and reliability thus for disintegrating machine propose significantly high requirement.
Disintegrating machine conventional at present has jaw, rotary type, hammer and reaction type etc..Jaw crusher is to utilize two jaws material is extruded and bends, and makes ratchel become a kind of batch (-type) breaker of small crushed stone；Gyratory crusher is to utilize broken cone to do in housing inner cone chamber to make material produce extruding, splitting and bending in turning motion, so that the Large Crusher tool of the Ore of various hardness or catalase；Hammer mill is the machinery utilizing the high speed impact effect of tup to make material broken；Impact breaker is utilize the high speed impact effect of bar and the rebound effect of counterpunch board and makes material be subject to repeated stock and broken machinery.These crushing mechanisms are generally adopted mechanical work mode, or rely on the extruding flecition of breaker to make material crush, and efficiency this kind broken is low, and the crushing effect for bulk materials is poor；Or adopt bar etc. that material is impacted and make material crush, the efficiency of this mode compares the high of squash type, but owing to the percussion in shattering process is very big, bearing etc. for disintegrating apparatus requires significantly high, and the control of impulsive force difficulty, easily occur that overshoot or bigger material are difficult to problems such as crushing.
Utility model content
Technical problem underlying to be solved in the utility model is a kind of to have higher crushing efficiency and the easily controllable hydraulic breaker hydraulic control system of shattering process.
In order to solve above-mentioned technical problem, this utility model provides a kind of crusher hydraulic and controls system, including:
Two hydraulic cylinders, drive a jump bit respectively；When the piston of wherein the first hydraulic cylinder is in maximum extended position, the piston of the second hydraulic cylinder is in minimum extended position；
Hydraulic pump, its outlet is connected with the entrance of the first check valve, and the outlet of the first check valve is connected with the entrance of ratio pressure flow compound control valve；The outlet of described ratio pressure flow compound control valve is connected with the P mouth of the one 3/4 solenoid directional control valve, the 2nd 3/4 solenoid directional control valve respectively；The independent oil sump tank of leakage hydraulic fluid port of ratio pressure flow compound control valve；
Described one 3/4 solenoid directional control valve, the 2nd 3/4 solenoid directional control valve T mouth communicated with fuel tank by the entrance of forced air cooler and the second check valve；The A mouth of the one 3/4 solenoid directional control valve and the P mouth of the 4th 3/4 solenoid directional control valve are connected, and the B mouth of the one 3/4 solenoid directional control valve and the P mouth of the 3rd 3/4 solenoid directional control valve are connected；The T mouth of the 4th 3/4 solenoid directional control valve and the A mouth of the 2nd 3/4 solenoid directional control valve are connected, and the T mouth of the 3rd 3/4 solenoid directional control valve and the B mouth of the 2nd 3/4 solenoid directional control valve are connected；
A Kou Fen tri-tunnel of described 4th 3/4 solenoid directional control valve, the first via is connected with the P mouth of the one 2/2 solenoid directional control valve, and the second tunnel is connected with the rod chamber of the second hydraulic cylinder, and the 3rd tunnel is connected with the second ball valve；The B mouth of the 4th 3/4 solenoid directional control valve and the first ball valve are connected；
3rd 3/4 solenoid directional control valve A Kou Fen tri-tunnel, the first via is connected with the rodless cavity of the first hydraulic cylinder, and the second tunnel is connected with the P mouth of the 2nd 2/2 solenoid directional control valve, and the 3rd tunnel is connected with another mouth of the first ball valve；The B mouth of the 3rd 3/4 solenoid directional control valve and the another port of the second ball valve are connected；
A Kou Fen tetra-tunnel of described one 2/2 solenoid directional control valve, the first via is connected with the rodless cavity of the first hydraulic cylinder, second tunnel is connected with the entrance of the first two-way flow speed control valve, and the 3rd tunnel is connected with the entrance of the first pressure switch, and the 4th tunnel is connected with the pressure tap of the second pressure transducer；
A Kou Fen tetra-tunnel of described 2nd 2/2 solenoid directional control valve, the first via is connected with the rodless cavity of the second hydraulic cylinder, second tunnel is connected with the entrance of the second two-way flow speed control valve, and the 3rd tunnel is connected with the entrance of the second pressure switch, and the 4th tunnel is connected with the pressure tap of the second pressure transducer；
Described first two-way flow speed control valve, the second two-way flow speed control valve outlet by the entrance oil sump tank of forced air cooler and the second check valve；The piston rod of the first hydraulic cylinder is provided with the first displacement transducer and the first travel switch roller；The piston rod of the second hydraulic cylinder is provided with second displacement sensor and the second travel switch roller；Described first hydraulic cylinder and the second hydraulic cylinder are provided with travel switch in the position corresponding with the maximum elongation position and minimum elongation position of piston rod.
In a preferred embodiment: described ratio pressure flow compound control valve includes flow and pressure dual control model, and output pressure and flow to hydraulic pump are controlled.
In a preferred embodiment: described first two-way flow speed control valve, the second two-way flow speed control valve are proportional velocity regulating valve, proportional according to input signal, regulate flow in real time.
Compared to prior art, the technical solution of the utility model possesses following beneficial effect:
A kind of crusher hydraulic that this utility model provides controls system, and two jump bits are respectively by two Driven by Hydraulic Cylinder.Under the control of four 3/4 solenoid directional control valves, two 2/2 solenoid directional control valves and two two-way flow speed control valves, make one in two jump bits that the piston rod of two hydraulic cylinders drives to move upward, and another moves downward and carries out impacting and the motion of broken material.Passing ratio compound control valve of pressure flowrate, the movement velocity of two hydraulic cylinder pistons can be adjusted, broken region interferes in bottom can to avoid two jump bits on the one hand, the operating frequency of disintegrating machine can be adjusted on the other hand, such that it is able to the material of different hardness is effectively crushed, improve work efficiency.And owing to have employed a kind of load-sensitive principle, crushing suddenly when bulk materials and make crushing force reduce suddenly, now hydraulic system can change by perception load pressure quickly, thus avoiding the appearance of overshoot, it is to avoid the excessive infringement to equipment of impulsive force.And when running into bulk materials and being difficult to broken, hydraulic system can export high pressure in short-term, material is carried out extruding and makes it crush, it is to avoid the repeated stock of jump bit, reduce the impact to system, and the crushing efficiency of disintegrating machine is greatly improved.This control system can adopt automated job mode, when after system start-up, it is possible to is automatically performed the broken work of reciprocating impact；And through certain setting time, can switch between different operating module, make components and parts be in discontinuous operation state, improve functional reliability；When part components and parts break down, it is possible to be replaced in non-stop-machine situation, improve the work efficiency of disintegrating machine.
Accompanying drawing explanation
Fig. 1 is the schematic diagram that in this utility model preferred embodiment, crusher hydraulic controls system.
Detailed description of the invention
Hereafter by the drawings and specific embodiments, this utility model is described further.
With reference to Fig. 1, a kind of crusher hydraulic controls system, including:
Two hydraulic cylinders, drive a jump bit respectively；When the piston of wherein the first hydraulic cylinder 13.1 is in maximum extended position, the piston of the second hydraulic cylinder 13.2 is in minimum extended position；
Hydraulic pump 4, its outlet is connected with the entrance of the first check valve 5, and the outlet of the first check valve 5 is connected with the entrance of ratio pressure flow compound control valve 6；The outlet of described ratio pressure flow compound control valve 6 is connected with the P mouth of the one 3/4 solenoid directional control valve the 7.1, the 2nd 3/4 solenoid directional control valve 7.2 respectively；The independent oil sump tank 1 of leakage hydraulic fluid port of ratio pressure flow compound control valve 6；
The T mouth of described one 3/4 solenoid directional control valve the 7.1, the 2nd 3/4 solenoid directional control valve 7.2 is communicated with fuel tank 1 by the entrance of forced air cooler 3 and the second check valve 3；The A mouth of the one 3/4 solenoid directional control valve 7.1 and the P mouth of the 4th 3/4 solenoid directional control valve are connected, and the B mouth of the one 3/4 solenoid directional control valve 7.1 and the P mouth of the 3rd 3/4 solenoid directional control valve are connected；The T mouth of the 4th 3/4 solenoid directional control valve and the A mouth of the 2nd 3/4 solenoid directional control valve 7.2 are connected, and the T mouth of the 3rd 3/4 solenoid directional control valve 7.3 and the B mouth of the 2nd 3/4 solenoid directional control valve 7.2 are connected；
A Kou Fen tri-tunnel of described 4th 3/4 solenoid directional control valve 7.4, the first via is connected with the P mouth of the one 2/2 solenoid directional control valve 10.1, and the second tunnel is connected with the rod chamber of the second hydraulic cylinder 13.2, and the 3rd tunnel is connected with the second ball valve 9.2；B mouth and first ball valve 9.1 of the 4th 3/4 solenoid directional control valve 7.4 are connected；
3rd 3/4 solenoid directional control valve 7.3 A Kou Fen tri-tunnel, the first via is connected with the rodless cavity of the first hydraulic cylinder 13.1, and the second tunnel is connected with the P mouth of the 2nd 2/2 solenoid directional control valve 10.2, and the 3rd tunnel is connected with another mouth of the first ball valve 9.1；The B mouth of the 3rd 3/4 solenoid directional control valve 7.3 and the another port of the second ball valve 9.2 are connected；
A Kou Fen tetra-tunnel of described one 2/2 solenoid directional control valve 10.1, the first via is connected with the rodless cavity of the first hydraulic cylinder 13.1, second tunnel is connected with the entrance of the first two-way flow speed control valve 8.1,3rd tunnel is connected with the entrance of the first pressure switch 11.1, and the 4th tunnel is connected with the pressure tap of the second pressure transducer 12.212.1；
A Kou Fen tetra-tunnel of described 2nd 2/2 solenoid directional control valve 10.2, the first via is connected with the rodless cavity of the second hydraulic cylinder 13.2, second tunnel is connected with the entrance of the second two-way flow speed control valve 8.2, and the 3rd tunnel is connected with the entrance of the second pressure switch 11.2, and the 4th tunnel is connected with the pressure tap of the second pressure transducer；
The outlet of described first two-way flow speed control valve the 8.1, the second two-way flow speed control valve 8.2 entrance oil sump tank 1 by forced air cooler 3 and the second check valve 3；The piston rod of the first hydraulic cylinder 13.1 is provided with the first displacement transducer 14.1 and the first travel switch roller；The piston rod of the second hydraulic cylinder 13.2 is provided with second displacement sensor 14.2 and the second travel switch roller；Described first hydraulic cylinder 13.1 is provided with travel switch 15.1,15.2,15.3,15.4 with the second hydraulic cylinder 13.2 in the position corresponding with the maximum elongation position and minimum elongation position of piston rod.
Described ratio pressure flow compound control valve 6 includes flow and pressure dual control model, and output pressure and flow to hydraulic pump 4 are controlled.Described first two-way flow speed control valve the 8.1, second two-way flow speed control valve 8.2 is proportional velocity regulating valve, proportional according to input signal, regulate flow in real time.
Control system below according to crusher hydraulic in the present embodiment in the different operating stage, the control of disintegrating machine to be described further.
(1) groundwork flow process:
State before starting: before disintegrating machine is started working, the piston of the first hydraulic cylinder 13.1 and the second hydraulic cylinder 13.2 is respectively at maximum extended position and minimum extended position.
First is stretched out/retracts stroke: when disintegrating machine is started working, and the left electric magnet 7.1a energising of the one 3/4 solenoid directional control valve 7.1, left position works；The right electric magnet 7.2b energising right position work of the 2nd 3/4 solenoid directional control valve 7.2；The right electric magnet 7.4b energising right position work of the 4th 3/4 solenoid directional control valve 7.4；The electric magnet energising of the one 2/2 solenoid directional control valve 10.1, left position works.The hydraulic oil of now hydraulic pump 4 output is through the first check valve 5, by ratio pressure flow compound control valve 6 according to the load suitable pressure of setting and flow, the right position of the hydraulic oil left position through the one 3/4 solenoid directional control valve 7.1 and the 4th 3/4 solenoid directional control valve 7.4, one road flows into the rod chamber of the second hydraulic cylinder 13.2, makes piston rod bounce back；Another road enters the rodless cavity of the first hydraulic cylinder 13.1 behind the left position of the one 2/2 solenoid directional control valve 10.1, makes piston rod stretch out, and drives jump bit to move to fracture area；Now, the oil of the rodless cavity of the second hydraulic cylinder 13.2 flows back to fuel tank 1 through the second two-way flow speed control valve 8.2；The hydraulic oil of the first hydraulic cylinder 13.1 rod chamber is through the right position oil sump tank 1 of the right position of the first ball valve the 9.1, the 4th 3/4 solenoid directional control valve 7.4, the 2nd 3/4 solenoid directional control valve 7.2.Owing to stretching out different with the active force that bears in retraction process and active area is different at two piston rods, necessarily cause that the movement velocity of piston is inconsistent.But loop has two flow-regulating components ratio pressure flow compound control valves 6 and the second two-way flow speed control valve 8.2；Ratio pressure flow compound control valve 6 have adjusted the total flow in system, and the input flow rate of the second hydraulic cylinder 13.2 set up by the second two-way flow speed control valve 8.2, namely the flow of the first hydraulic cylinder 13.1 and the second hydraulic cylinder 13.2 is certain, therefore movement velocity and the movement time of two hydraulic cylinder pistons can be controlled easily, such that it is able to avoid the interference in broken region of two jump bits.And passing ratio compound control valve of pressure flowrate 6 and the adjustment to flow of the second two-way flow speed control valve 8.2, in that context it may be convenient to adjust the movement velocity of piston, thus effectively controlling break-up frequency.
Second is stretched out/retracts stroke: when the piston rod of the first hydraulic cylinder 13.1 reach maximum position carry out broken time, now encounter travel switch 15.2, and the piston rod of the second hydraulic cylinder 13.2 retract to minimum after, encounter travel switch 15.4；And now the first pressure switch 11.1 does not have action, illustrating not run in shattering process hard material, material normally crushes.Now under the effect of travel switch 15.2 and 15.4, the left electric magnet 7.4a energising left position work of the 4th 3/4 solenoid directional control valve 7.4, the electric magnet power-off of the one 2/2 solenoid directional control valve 10.1, the electric magnet energising of the 2nd 2/2 solenoid directional control valve 10.2, the next work；The pressure oil of now hydraulic pump 4 output is through the first check valve 5, by ratio pressure flow compound control valve 6 according to the load suitable pressure of setting and flow, hydraulic oil is through the left position of the one 3/4 solenoid directional control valve 7.1 and the left position of the 4th 3/4 solenoid directional control valve 7.4 and the first ball valve 9.1, one road flows into the rod chamber of the first hydraulic cylinder 13.1, makes piston rod bounce back；Another road enters the rodless cavity of the second hydraulic cylinder 13.2 behind the bottom of the 2nd 2/2 solenoid directional control valve 10.2, makes piston rod stretch out, and drives jump bit to move to fracture area.Now, the hydraulic oil of the rod chamber of the first hydraulic cylinder 13.1 is through the first two-way flow speed control valve 8.1 oil sump tank 1；The hydraulic oil of the second hydraulic cylinder 13.2 rodless cavity through the left position of the 4th 3/4 solenoid directional control valve 7.4, the 2nd 3/4 7.2 right oil sump tanks of solenoid directional control valve 1.In the process, the flow of the first hydraulic cylinder 13.1 and the input of the second hydraulic cylinder 13.2 can be set up by ratio pressure flow compound control valve 6 and the second two-way flow speed control valve 8.2, therefore the movement velocity of two piston rods can be controlled accurately, thus avoiding the interference in broken region of two jump bits, and passing ratio compound control valve of pressure flowrate 6 and the adjustment to flow of the second two-way flow speed control valve 8.2, the movement velocity of piston can be adjusted easily, thus effectively controlling break-up frequency.
When the piston rod of the first hydraulic cylinder 13.1 encounters travel switch 15.1, the piston rod of the second hydraulic cylinder 13.2 encounters travel switch 15.3, and now pressure switch 11.2 does not have action, illustrates not run in shattering process hard material, and material normally crushes；Now under the effect at travel switch 15.1 and 15.3, the right electric magnet 7.4b energising right position work of the 4th 3/4 solenoid directional control valve 7.4, the electric magnet power-off of the 2nd 2/2 solenoid directional control valve 10.2, the electric magnet energising of the one 2/2 solenoid directional control valve 10.1, left position works.Now two hydraulic cylinder pistons return to initial position, complete a basic cycle of operation.
In the process, what be in frequent commutation states is the 4th 3/4 solenoid directional control valve 7.4, electromagnetic valve the 1st solenoid directional control valve the 10.1 and the 2nd 2/2 solenoid directional control valve 10.2；But owing to the one 2/2 solenoid directional control valve the 10.1 and the 2nd 2/2 solenoid directional control valve 10.2 adopts plug-in structure, commutation action is fast, safe and reliable.
(2) operational module switching
Owing to the working strength of disintegrating machine is big, each solenoid directional control valve is in continuous switching state, in order to ensure the reliably working of each solenoid directional control valve, extend the service life of various solenoid directional control valve, need to make the reversal valve rest certain time of participation work through the regular hour；And in order to not affect production efficiency, disintegrating machine can not quit work, now it is accomplished by another group solenoid directional control valve participation work.Now the one 3/4 solenoid directional control valve is to the right electric magnet 7.1b energising right position work of valve 7.1, and the electric magnet of the 3rd 3/4 solenoid directional control valve electromagnetic valve 7.3 switches in reciprocating motion of the pistons process, position, left and right sequential working, and the job order of its hydraulic circuit is:
Hydraulic pump 4-the first check valve 5-ratio pressure flow compound control valve 6-the 1st solenoid directional control valve is to the right position of valve 7.1-3 3/4 solenoid directional control valve to the left position of valve 7.3-the second ball valve 9.2；Oil circuit divides two-way, the left bit stream of one tunnel the 1st solenoid directional control valve 10.1 enters the rodless cavity of the first hydraulic cylinder 13.1, the rod chamber hydraulic oil of the first hydraulic cylinder 13.1 through the 3rd 3/4 solenoid directional control valve to left position-the 2 3/4 solenoid directional control valve of valve 7.3 to the left position oil sump tank 1 of valve 7.2；Another road flows directly into the rod chamber of the second hydraulic cylinder 13.2, and the hydraulic oil of the second hydraulic cylinder 13.2 rodless cavity is through the second two-way flow speed control valve 8.2 oil sump tank 1；
When piston commutation motion, its oil circuit order is:
Hydraulic pump 4-the first check valve 5-ratio pressure flow compound control valve 6-the 1st solenoid directional control valve is to the right position of valve 7.1-3 3/4 solenoid directional control valve to the right position of valve 7.3；Oil circuit divides two-way, and a road is directly entered the rod chamber of the first hydraulic cylinder 13.1, and the hydraulic oil of the one 13.1 rodless cavity is through the first direct oil sump tank 1 of two-way flow speed control valve 8.1；The next rodless cavity entering the second hydraulic cylinder 13.2 of another road the 2nd 2/2 solenoid directional control valve 10.2, the second hydraulic cylinder 13.2 rod chamber hydraulic oil through the second ball valve 9.2-the 3rd 3/4 solenoid directional control valve to the right position of valve 7.3-the 2 3/4 solenoid directional control valve to 7.2 left oil sump tanks of valve 1.
Namely in this cyclic process, be in frequent commutation states be the 3rd 3/4 solenoid directional control valve to valve 7.3, the one 2/2 solenoid directional control valve the 10.1 and the 2nd 2/2 solenoid directional control valve 10.2；But owing to the one 2/2 solenoid directional control valve the 10.1 and the 2nd 2/2 solenoid directional control valve 10.2 adopts plug-in structure, commutation action is fast, safe and reliable.
Therefore the 3rd 3/4 solenoid directional control valve the 7.3 and the 4th 3/4 solenoid directional control valve can be made by the way in running order in turn to valve 7.4, reduce the working strength of solenoid directional control valve, extend its service life, improve job security.
(3) intelligent booster crushes
When jump bit runs into harder material, when one-shot is difficult to broken, now the pressure of hydraulic cylinder raises, pressure switch action, postpones piston rod commutation, signal by the pressure transducer obtained and displacement transducer, ratio pressure flow compound control valve 6 pressure raises in short-term, improves the input pressure of hydraulic cylinder, relies on powerful extruding in short-term to make material crush, reduce the repeated stock action of jump bit, improve crushing efficiency.
(4) fault does not shut down guarantee
First ball valve 9.1 and the second ball valve 9.2 are to prevent the wherein way solenoid valve from breaking down, it is to avoid disintegrating machine entirety is shut down and arranged.If the 3rd 3/4 solenoid directional control valve 7.3 breaks down, now the second ball valve 9.2 is closed, 3rd 3/4 solenoid directional control valve 7.3 is carried out disassembling, assembling and replacing, without affecting the normal operation of the first hydraulic cylinder 13.1 and the second hydraulic cylinder 13.2, equally, the first ball valve 9.1 is to arrange in order to the 4th 3/4 solenoid directional control valve 7.4 is carried out disassembling, assembling and replacing.
(5) Load-aware function
When running into harder material, the stress of hydraulic cylinder increases, and flow reduces, now flow passing ratio flow pressure compound control valve 6 oil sump tank 1 of system；When material broken moment, although hydraulic cylinder pressure is die-offed, but owing to flow can not feed at once, piston rod can not preshoot；And now pressure switch resets owing to pressure reduces, and triggering corresponding electric magnet and cause that piston rod commutate, drive jump bit adverse movement, thus avoiding the jump bit impact to system.
(6) fluid intelligence cooling
Of many uses due to disintegrating machine, is therefore used in China broad area, and this working environment difference also leading to disintegrating machine is very big, especially temperature very different.And for hydraulic system, its working media is extremely sensitive for the change of temperature, such hydraulic oil flow resistance when flowing through pipeline will change.For ensure system hydraulic oil in certain temperature range, native system devises a forced air cooler 3, and it is in parallel with second check valve 2.When system temperature is lower than design temperature, oil return is through the second check valve 2 oil sump tank 1, and now forced air cooler 3 does not work；And after the temperature of hydraulic oil exceedes certain value, the now shunting action according to hydraulic oil, a part of hydraulic oil is through forced air cooler 3 oil sump tank 1, hydraulic oil is made to be cooled down, along with the rising of hydraulic fluid temperature, the rotating speed of forced air cooler 3 improves therewith, strengthens the cooling effect of hydraulic oil.
The above; it is only this utility model preferably detailed description of the invention; but protection domain of the present utility model is not limited thereto; any those familiar with the art is in the technical scope that this utility model discloses; the change that can readily occur in or replacement, all should be encompassed within protection domain of the present utility model.Therefore, protection domain of the present utility model should be as the criterion with scope of the claims.
Claims (3)
1. a crusher hydraulic controls system, it is characterised in that including:
Two hydraulic cylinders, drive a jump bit respectively；When the piston of wherein the first hydraulic cylinder is in maximum extended position, the piston of the second hydraulic cylinder is in minimum extended position；
Hydraulic pump, its outlet is connected with the entrance of the first check valve, and the outlet of the first check valve is connected with the entrance of ratio pressure flow compound control valve；The outlet of described ratio pressure flow compound control valve is connected with the P mouth of the one 3/4 solenoid directional control valve, the 2nd 3/4 solenoid directional control valve respectively；The independent oil sump tank of leakage hydraulic fluid port of ratio pressure flow compound control valve；
Described one 3/4 solenoid directional control valve, the 2nd 3/4 solenoid directional control valve T mouth communicated with fuel tank by the entrance of forced air cooler and the second check valve；The A mouth of the one 3/4 solenoid directional control valve and the P mouth of the 4th 3/4 solenoid directional control valve are connected, and the B mouth of the one 3/4 solenoid directional control valve and the P mouth of the 3rd 3/4 solenoid directional control valve are connected；The T mouth of the 4th 3/4 solenoid directional control valve and the A mouth of the 2nd 3/4 solenoid directional control valve are connected, and the T mouth of the 3rd 3/4 solenoid directional control valve and the B mouth of the 2nd 3/4 solenoid directional control valve are connected；
A Kou Fen tri-tunnel of described 4th 3/4 solenoid directional control valve, the first via is connected with the P mouth of the one 2/2 solenoid directional control valve, and the second tunnel is connected with the rod chamber of the second hydraulic cylinder, and the 3rd tunnel is connected with the second ball valve；The B mouth of the 4th 3/4 solenoid directional control valve and the first ball valve are connected；
3rd 3/4 solenoid directional control valve A Kou Fen tri-tunnel, the first via is connected with the rodless cavity of the first hydraulic cylinder, and the second tunnel is connected with the P mouth of the 2nd 2/2 solenoid directional control valve, and the 3rd tunnel is connected with another mouth of the first ball valve；The B mouth of the 3rd 3/4 solenoid directional control valve and the another port of the second ball valve are connected；
A Kou Fen tetra-tunnel of described one 2/2 solenoid directional control valve, the first via is connected with the rodless cavity of the first hydraulic cylinder, second tunnel is connected with the entrance of the first two-way flow speed control valve, and the 3rd tunnel is connected with the entrance of the first pressure switch, and the 4th tunnel is connected with the pressure tap of the second pressure transducer；
A Kou Fen tetra-tunnel of described 2nd 2/2 solenoid directional control valve, the first via is connected with the rodless cavity of the second hydraulic cylinder, second tunnel is connected with the entrance of the second two-way flow speed control valve, and the 3rd tunnel is connected with the entrance of the second pressure switch, and the 4th tunnel is connected with the pressure tap of the second pressure transducer；
Described first two-way flow speed control valve, the second two-way flow speed control valve outlet by the entrance oil sump tank of forced air cooler and the second check valve；The piston rod of the first hydraulic cylinder is provided with the first displacement transducer and the first travel switch roller；The piston rod of the second hydraulic cylinder is provided with second displacement sensor and the second travel switch roller；Described first hydraulic cylinder and the second hydraulic cylinder are provided with travel switch in the position corresponding with the maximum elongation position and minimum elongation position of piston rod.
2. a kind of crusher hydraulic as claimed in claim 1 controls system, it is characterised in that: described ratio pressure flow compound control valve includes flow and pressure dual control model, and output pressure and flow to hydraulic pump are controlled.
3. crusher hydraulic as claimed in claim 1 a kind of controls system, it is characterised in that: described first two-way flow speed control valve, the second two-way flow speed control valve are proportional velocity regulating valve, proportional according to input signal, regulate flow in real time.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620146332.5U CN205401282U (en) | 2016-02-26 | 2016-02-26 | Breaker hydraulic control system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620146332.5U CN205401282U (en) | 2016-02-26 | 2016-02-26 | Breaker hydraulic control system |
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| CN205401282U true CN205401282U (en) | 2016-07-27 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201620146332.5U Withdrawn - After Issue CN205401282U (en) | 2016-02-26 | 2016-02-26 | Breaker hydraulic control system |
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| CN105545847A (en) * | 2016-02-26 | 2016-05-04 | 华侨大学 | Hydraulic control system of crusher |
| CN108105175A (en) * | 2016-11-25 | 2018-06-01 | 天津科企生产力促进有限公司 | Pass through the automatically controlled pressure relief mechanism of overflow valve pressurize |
| CN108105177A (en) * | 2016-11-25 | 2018-06-01 | 天津凡旋科技有限公司 | Automatically controlled pressure relief mechanism with dual buck functionality |
| CN108105178A (en) * | 2016-11-25 | 2018-06-01 | 天津凤宜科技有限公司 | There is differential automatically controlled pressure relief mechanism |
| CN109201303A (en) * | 2018-09-18 | 2019-01-15 | 中山斯瑞德环保科技股份有限公司 | A kind of optimal control method improving hydraulic breaker crushing efficiency |
| CN110005014A (en) * | 2019-05-07 | 2019-07-12 | 徐州徐工挖掘机械有限公司 | It is a kind of can automatic frequency adjustment quartering hammer hydraulic system, control method and excavator |
| CN111201087A (en) * | 2017-10-25 | 2020-05-26 | 克磊镘有限公司 | Method for load dependent operation of a material comminution system |
| CN111482262A (en) * | 2020-04-15 | 2020-08-04 | 天能电池(芜湖)有限公司 | Control mode for improving stability of lead powder ball milling |
| CN112128176A (en) * | 2020-08-27 | 2020-12-25 | 中联重科股份有限公司 | Engineering machinery power adjusting method based on displacement detection and hydraulic power system |
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2016
- 2016-02-26 CN CN201620146332.5U patent/CN205401282U/en not_active Withdrawn - After Issue
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| CN105545847B (en) * | 2016-02-26 | 2017-07-21 | 华侨大学 | crusher hydraulic control system |
| CN105545847A (en) * | 2016-02-26 | 2016-05-04 | 华侨大学 | Hydraulic control system of crusher |
| CN108105175A (en) * | 2016-11-25 | 2018-06-01 | 天津科企生产力促进有限公司 | Pass through the automatically controlled pressure relief mechanism of overflow valve pressurize |
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| CN111201087A (en) * | 2017-10-25 | 2020-05-26 | 克磊镘有限公司 | Method for load dependent operation of a material comminution system |
| CN109201303A (en) * | 2018-09-18 | 2019-01-15 | 中山斯瑞德环保科技股份有限公司 | A kind of optimal control method improving hydraulic breaker crushing efficiency |
| CN110005014A (en) * | 2019-05-07 | 2019-07-12 | 徐州徐工挖掘机械有限公司 | It is a kind of can automatic frequency adjustment quartering hammer hydraulic system, control method and excavator |
| CN110005014B (en) * | 2019-05-07 | 2023-06-27 | 徐州徐工挖掘机械有限公司 | Breaking hammer hydraulic system capable of automatically adjusting frequency, control method and excavator |
| CN111482262A (en) * | 2020-04-15 | 2020-08-04 | 天能电池(芜湖)有限公司 | Control mode for improving stability of lead powder ball milling |
| CN111482262B (en) * | 2020-04-15 | 2021-09-28 | 天能电池(芜湖)有限公司 | Control mode for improving stability of lead powder ball milling |
| CN112128176A (en) * | 2020-08-27 | 2020-12-25 | 中联重科股份有限公司 | Engineering machinery power adjusting method based on displacement detection and hydraulic power system |
| CN112128177A (en) * | 2020-08-27 | 2020-12-25 | 中联重科股份有限公司 | Method for dynamically adjusting engineering machinery power |
| CN112128176B (en) * | 2020-08-27 | 2022-04-19 | 中联重科股份有限公司 | Engineering machinery power adjusting method based on displacement detection and hydraulic power system |
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