CN1515800A - Hydraulic circuit and control method for rotary breaker - Google Patents
Hydraulic circuit and control method for rotary breaker Download PDFInfo
- Publication number
- CN1515800A CN1515800A CNA2003101043326A CN200310104332A CN1515800A CN 1515800 A CN1515800 A CN 1515800A CN A2003101043326 A CNA2003101043326 A CN A2003101043326A CN 200310104332 A CN200310104332 A CN 200310104332A CN 1515800 A CN1515800 A CN 1515800A
- Authority
- CN
- China
- Prior art keywords
- pressure
- oil
- oil hydraulic
- working oil
- hydraulic cylinder
- 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.)
- Granted
Links
- 238000000034 method Methods 0.000 title claims description 14
- 230000002159 abnormal effect Effects 0.000 claims abstract description 15
- 238000013467 fragmentation Methods 0.000 claims description 7
- 238000006062 fragmentation reaction Methods 0.000 claims description 7
- 238000007599 discharging Methods 0.000 claims 2
- 238000011084 recovery Methods 0.000 claims 1
- 230000002964 excitative effect Effects 0.000 description 13
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 10
- 239000012530 fluid Substances 0.000 description 7
- 230000015572 biosynthetic process Effects 0.000 description 5
- 230000000903 blocking effect Effects 0.000 description 5
- 239000002828 fuel tank Substances 0.000 description 5
- 229910052742 iron Inorganic materials 0.000 description 5
- 239000002994 raw material Substances 0.000 description 5
- 230000000694 effects Effects 0.000 description 4
- 239000011435 rock Substances 0.000 description 4
- 239000007788 liquid Substances 0.000 description 3
- 239000000463 material Substances 0.000 description 3
- 238000012856 packing Methods 0.000 description 3
- 230000000630 rising effect Effects 0.000 description 3
- 238000010521 absorption reaction Methods 0.000 description 2
- 230000006837 decompression Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000001771 impaired effect Effects 0.000 description 2
- 238000012423 maintenance Methods 0.000 description 2
- 239000002245 particle Substances 0.000 description 2
- 230000004043 responsiveness Effects 0.000 description 2
- 230000000007 visual effect Effects 0.000 description 2
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000009931 harmful effect Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000001404 mediated effect Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
Landscapes
- Fluid-Pressure Circuits (AREA)
- Crushing And Grinding (AREA)
- Disintegrating Or Milling (AREA)
Abstract
The hydraulic cylinder supporting a main shaft communicates with a main hydraulic line for supplying the working oil discharged from a hydraulic pump without interposing an accumulator. A pilot relief valve to which a pilot pressure is supplied from a pilot pressure supply line is provided in the hydraulic cylinder. When the abnormal pressure is produced in the hydraulic cylinder, the pilot pressure is released to relieve the working oil in the hydraulic cylinder and after the abnormal pressure is released, the pilot pressure is increased to close the pilot relief valve and the working oil is supplied from the main oil pressure line to return the pressure of the working oil in the hydraulic cylinder to the prescribed pressure.
Description
Technical field
The present invention relates to the controlling method of oil hydraulic circuit and this oil hydraulic circuit of gyratory crusher.
Background technique
For the oil hydraulic cylinder that main shaft is supported of the gyratory crusher of fractured rock or ore etc., supply with working oil by the main hydraulic line of oil hydraulic circuit.In broken process, thereby if make main shaft bear the pressure anomaly rising that excessive load causes working oil in the oil hydraulic cylinder because of blocking foreign matters such as iron plate, then can cause harmful effect, but also can bear bad phenomenon such as the oil film of sliding bearing of the axial force that acts on main shaft is withered the pipe arrangement of oil hydraulic cylinder, oil hydraulic circuit or equipment etc.
It is known with the disintegrator of the abnormal pressure that produced in the absorption liquid cylinder pressure that accumulator is set in main hydraulic line for this reason.Be the piston that produces at hydraulic pressure on carry out under the thrust, situation about balancing each other with the axial thrust load of, the crushing force that produced when carrying out fragmentation broken, but when block foreign matter or because of the density of the broken thing in the overcrushing crushing chamber than contemplated when big, the load that produces because of crushing force is excessive will act on main shaft, and disintegrator integral body will be born excessive load.Its result, its oil film of sliding bearing that not only bears the axial force of main shaft is difficult to form, and can cause disintegrator impaired.
At this situation; the impact that produces in accumulator and the relief valve hydraulic piping with the absorption liquid hydraulic circuit or the hydraulic pressure of releasing are set in oil hydraulic circuit; thereby to the gyratory crusher that body is protected known (for example, the spy opens flat 10-272375 communique).
In addition, in main hydraulic line, accumulator is set, when the pressure of working oil reduces, main shaft is risen and make the exhaust port of broken goods narrow down, make exhaust port become greatly to reduce load a kind of like this disintegrator known (for example special public clear 56-36981 communique) and main shaft is descended to increase load.
As above-mentioned disintegrator, when the excessive hydraulic pressure that produces in the oil hydraulic cylinder greater than the gas pressure of accumulator air bag, working oil will flow in the accumulator (ア キ エ system レ one ), and till pressure in main hydraulic line and the airbag gas pressure balance, the pressure of working oil will raise in this pipeline.In addition, the occasion that the pressure in oil hydraulic cylinder raises rapidly will wait until that working oil flows in the accumulator, working fluid pressure reaches balance with airbag gas pressure, the hysteresis on the life period, and during this period, the pressure in the oil hydraulic cylinder will continue rising.Its result, disintegrator integral body will keep overload state, and the formation of its oil film of sliding bearing that the lower end surface of main shaft is supported is hindered, thereby the problem of burn bearing can take place.In the great occasion of the load that is produced, the stress that might make under the overload state to be produced surpasses design strength, even it is impaired to develop into disintegrator integral body.
Carry out the pressure of balance with working fluid pressure, by the pressure decision of envelope gas in the accumulator, but when the temperature difference cause that gas pressure changes or, during along with time lapse gas pressure reduction, the pressure that carries out balance also can change.The main shaft holding power will change thereupon, and therefore, crushing performance will change.In addition, strengthen the caliber of main hydraulic line, though can improve the responsiveness of accumulator, thereby the problem that brought time lag can improve, still, because the working oil oil mass increases in the main hydraulic line, be subjected to the influence of the volume elasticity rate of working oil, the internal volume of oil hydraulic cylinder can change, and this will cause piston that fluctuation takes place and become unstable, can not carry reliably because of carrying out the crushing force that fragmentation produces.Therefore, can't make the density of interior rock of crushing chamber or ore keep certain, can't obtain stable broken goods.That is to say, can produce problems such as crushing performance instability, broken Products Quality reduction.
In addition, drive the disintegrator that clear 56-36981 communique is put down in writing as the spy, material density in crushing chamber increases and the pressure of working oil occasion jumpy in the oil hydraulic cylinder, main shaft is descended but the speed that descends is slower by the traction of oil hydraulic pump, thereby can't avoid the pressure of working oil in the oil hydraulic cylinder to raise, cause being in the crushing chamber packing state.Its result, disintegrator can be shut down under filling has the situation of raw material, thereby can't stably carry out operation continuously.
Disclosure of an invention
The objective of the invention is, provide a kind of, the abnormal pressure that is produced in the oil hydraulic cylinder that main shaft is supported can be released rapidly and make the pressure of working oil in the oil hydraulic cylinder return to set pressure rapidly, thereby can carry out operation sustainedly and stably, and can make the oil hydraulic circuit of the guaranteed gyratory crusher of broken Products Quality and the controlling method of this oil hydraulic circuit.
The oil hydraulic circuit of gyratory crusher of the present invention has following basic comprising.
That is, belong to a kind of oil hydraulic circuit that can freely adjust the oil hydraulic cylinder supply working oil of its upper-lower position to the main shaft (main shaft) with broken cycle with cone part is supported and can make the certain gyratory crusher of the pressure maintenance of working oil in the oil hydraulic cylinder.This oil hydraulic circuit has, and supplies with the oil hydraulic pump of working oil to oil hydraulic circuit, and, the main hydraulic line that will supply with to oil hydraulic cylinder from the working oil that this oil hydraulic pump extrudes.This oil hydraulic pump is not communicated with via accumulator with oil hydraulic cylinder.Have again, this oil hydraulic circuit has, and makes the pilot relief valve of the working oil overflow in the oil hydraulic cylinder by the pilot pressure of releasing, and supplies with the pilot pressure supply pipeline of pilot pressure to pilot relief valve, and, the pilot pressure of the pilot pressure of the pilot pressure supply pipeline of the releasing pipeline of releasing.
In this occasion, oil hydraulic circuit and controlling method thereof according to gyratory crusher of the present invention, by make in the oil hydraulic cylinder working oil through the pilot relief valve overflow so that the abnormal pressure in this oil hydraulic cylinder reduce, make and in main hydraulic line, accumulator to be set that just the invention that can put down in writing than above-mentioned communique far is that the abnormal pressure in the oil hydraulic cylinder is reduced.Therefore, needn't worry that the formation of its oil film of sliding bearing that the lower end surface of main shaft is supported is hindered, problem such as needn't worry can take place that this sliding bearing is burnt to death.Have again,, also can eliminate immediately and exceed the such overload state of design strength, therefore, needn't worry that gyratory crusher integral body sustains damage even in the great occasion of load that produces.
Brief description of drawings
Fig. 1 is the hydraulic circuit diagram of the related gyratory crusher of the present invention's the 1st form of implementation.
Fig. 2 is the sectional view of the pilot relief valve in this form of implementation.
Fig. 3 is the operation conditions explanatory drawing of the gyratory crusher in this form of implementation.
Fig. 4 is the explanatory drawing of the operation conditions of the related gyratory crusher of the present invention's the 2nd form of implementation.
Best form of implementation
Oil hydraulic circuit to the related gyratory crusher of an embodiment of the present invention describes in conjunction with Fig. 1～4.This is a kind of form of implementation of the present invention, is not limited thereto.
Gyratory crusher has, and possesses broken rotatable main shaft with cone part, can freely adjust the oil hydraulic cylinder of its upper-lower position to main shaft support.This gyratory crusher is also referred to as hydraulic pressure cone disintegrator.
At first, describe with regard to the 1st form of implementation of the present invention.Fig. 1 is the hydraulic circuit diagram of gyratory crusher, and Fig. 2 is the sectional view of pilot relief valve, and Fig. 3 is the operation conditions explanatory drawing of gyratory crusher.
This disintegrator has not shown fragmentation cone part.The main shaft 20 of disintegrator constitutes rotating.Numbering 10 among Fig. 1 is oil hydraulic cylinder (abbreviating cylinder in the following description sometimes as), and main shaft 20 is supported freely to adjust its upper-lower position.This oil hydraulic cylinder 10 has by the piston 11 separated pressure chambers 12 that main shaft 20 is supported.This pressure chamber 12 constitutes like this, that is, be to keep certain oil hydraulic circuit 1 to supply with working oil by the pressure that makes the working oil in the pressure chamber 12.
Oil hydraulic circuit 1 has main hydraulic line 2.This pipeline 2 is communicated with the pressure chamber 12 of oil hydraulic cylinder 10 without accumulator, and the working oil that extrudes from oil hydraulic pump 2a is provided via electromagnetic type the 1st switch valve 2b.
The pressure of working oil in this pipeline 2 is monitored by the 1st visual pressure meter 2c and the 1st pressure transducer 2d that are installed on the branched pipe that comes out from the 1st switch valve 2b and the line branches between the oil hydraulic cylinder 10 of this pipeline 2.And the detected working fluid pressure of this sensor 2d inputs to programming controller 30 described later.
In addition, the 1st pressure transducer 2d detects the pressure of working oil in the main hydraulic line 2.On the other hand, can also connect like this, that is,, connect the hydraulic tube of oil hydraulic cylinder 10, and connect sensor 2d at the front end of this hydraulic tube for the pressure to working oil in the pressure chamber 12 detects.
Cylinder cap 13 is to be used for the bottom of liquid for plugging cylinder pressure 10.On this cylinder cap 13, be provided with the pilot relief valve 3 that makes the working oil overflow in the pressure chamber 12.On this pilot relief valve 3, there is the pilot pressure supply pipeline 4 that comes out from main hydraulic line 2 branches between oil hydraulic pump 2a and the 1st switch valve 2b to be communicated with it.Among this supply pipeline 4,34 cross valve 4b of electromagnetic type are installed.When this changing valve 4b mediated, the working oil that oil hydraulic pump 2a extrudes was returned working oil fuel tank 8 through working oil oil return pipeline 6.In this pipeline 6 oil purifier 6a is installed.
In addition, stroke detector 9 can be oily close state from downside and pass from cylinder cap 13, inserts in the hole set on the piston 11.The shift motion (being equivalent to position of piston) of the trip detector 9 detected pistons 11 also inputs to programming controller 30.That is to say, when the shift motion checkout value from stroke detector 9 reaches the highest setting value, main shaft 20 is descended.And when in the decline process, reaching minimum setting value, main shaft 20 is risen.
The pilot pressure of supplying with to pilot relief valve 3 by the conversion (solenoid of left side L is excitatory) of changing valve 4b is monitored by the 2nd visual pressure meter 4c and the 2nd pressure transducer 4d that are installed in from the branched pipe of the line branches between changing valve 4b and the pilot relief valve 3.The detected pilot pressure of this sensor 4d, same with the detected working fluid pressure of the 1st pressure transducer 2d, input to programming controller 30.In addition, from the branched pipe of the line branches between changing valve 4b and the pilot relief valve 3, compensation that pilot pressure is compensated is installed with accumulator (capacity is 1 liter) 4e.
Solenoidal excitatory to changing valve 4b right side R is to carry out when oil hydraulic cylinder 10 is supplied with working oil by main hydraulic line 2.
In addition, relief valve 3g is connected being connected on the connecting end that working oil oil return pipeline 6 gets on of pipeline 4.This relief valve 3g adjusts the pressure of working oil.Relief valve 3g can to the pilot pressure of supplying with pilot pressure supply pipeline 4 and, the pressure of supplying with the working oil of main hydraulic line 2 adjusts.
Near the outlet of the changing valve 4b of pilot pressure supply pipeline 4, branch out the pilot pressure that electromagnetic type the 2nd switch valve 5a wherein the is installed pipeline 5 of releasing.So, open and will be returned working oil fuel tank 8 via the working oil oil return pipeline 6 that oil purifier 6a wherein is installed by the pilot pressure of being released by this switch valve 5a.In addition,, can make working oil in the pressure chamber 12 of pilot relief valve 3 overflows by switch valve 5a is opened the pilot pressure of releasing, via oil overflow flow out pipeline 7, working oil oil return pipeline 6 returns working oil fuel tank 8.
Programming controller 30, in the detected main hydraulic line 2 of the 1st pressure transducer 2d the pressure of working oil, be the pressure of working oil in the pressure chamber 12, when surpassing predefined pressure set points because of blocking foreign matters such as iron plate, the solenoid of the 2nd switch valve 5a is carried out excitatory, this switch valve 5a is opened.Touch screen 31 is connected on the programming controller 30.This screen 31 is input states (input state of the ON of signal (leading to), OFF (breaking) attitude and temperature, pressure) of being used for showing the signal of importing in not shown control panel and the operation of gyratory crusher operated.
As shown in Figure 2, pilot relief valve 3 has, and downside has the seat accessory 3a and the taper valve core 3b of the seat of end chap.This taper valve core 3b is provided with like this,, is subjected to the active force of helical spring 3c towards accessory 3a seat direction that is.When passing through this pilot relief valve 3, the feasible last thrust of supplying with to pilot pressure port 3d that pilot pressure produced to taper valve core 3b, greater than work by working oil outflow port 3f, in the pressure chamber 12 during the following thrust that pressure produced of working oil, taper valve core 3b can not fall thereby continue the maintenance closed condition.And in case pilot pressure is released pipeline 5 when releasing through pilot pressure, the last thrust that taper valve core 3b is subjected to will be less than the following thrusts that pressure produced that work by working oil outflow port 3f, pressure chamber's 12 interior working oil.So taper valve core 3b falls, make the working oil overflow in the pressure chamber 12.By this overflow, the working oil in the pressure chamber 12 that tank port 3e flows out will flow out pipeline 7 from oil overflow and return working oil fuel tank 8.
Secondly, the effect to oil hydraulic circuit 1 describes.At first, the kind of operation control has main shaft operation control, main shaft 5 kinds of operation control, general operation control, pilot pressure pressurization control and the pilot pressure decompression controls (making working oil from the pilot relief valve overflow) etc. that descend of rising.Under each control kind, the Push And Release of the operation of oil hydraulic pump 2a, the 1st switch valve 2b, changing valve 4b, the 2nd switch valve 5a and pilot relief valve 3 carries out according to table 1.
Table 1
| Main shaft rises and moves control | Main shaft descends and moves control | General operation control | The pilot pressure pressurization control | Pilot pressure decompression control | |
| Oil hydraulic pump 2a | Just change | Counter-rotating | Stop | Just change | Stop |
| Switch valve 2b | ????ON | ????ON | ????OFF | ????OFF | ????OFF |
| Changing valve 4bR | ????ON | ????OFF | ????OFF | ????OFF | ????OFF |
| Changing valve 4bL | ????OFF | ????OFF | ????OFF | ????ON | ????OFF |
| Switch valve 5a | ????OFF | ????OFF | ????OFF | ????OFF | ????ON |
| Relief valve 3 | Close | Close | Close | Close | Open |
Under pilot relief valve 3 closing state, carry out general operation control, the main shaft rise and fall operation control (comprising main shaft lifting operation repeatedly) of disintegrator.In addition, in the table 1, ON represents the solenoid of valve excitatory (opening), and OFF represents to stop to the solenoid of valve excitatory (closing).
Here, generally in service for shown in the table 1 is because of the control of blocking under reasons such as foreign matter such as iron plate produce abnormal pressure in oil hydraulic cylinder 10 the situation describes.
(1) the 1st pressure transducer 2d that the pressure of working oil in the main hydraulic line 2 is detected detects the pressure more than the pressure set points.
(2) carry out excitatoryly to being installed in the release solenoid of the 2nd switch valve 5a among the pipeline 5 of pilot pressure, the 2nd switch valve 5a is opened.
(3) released because of pilot pressure and opened along with pilot relief valve 3, the working oil overflow in the oil hydraulic cylinder 10.Its result, the pressure of working oil reduces in the oil hydraulic cylinder 10.So main shaft 20 descends, exhaust port broadens, thereby can be with the discharges such as foreign matter such as iron plate that cause that pressure raises.
(4) the 1st pressure transducer 2d that the pressure of working oil in the main hydraulic line 2 is detected detects the pressure below the pressure set points.
(5) stop the 2nd switch valve 5a being closed to being installed in the solenoidal excitatory of the 2nd switch valve 5a among the pipeline 5 of releasing.
(6) oil hydraulic pump 2a is just changeed.
(7) the L side solenoid that is installed in the changing valve 4b among the pilot pressure supply pipeline 4 is carried out excitatory, in the oil hydraulic cylinder 10 that is produced when pilot pressure being elevated to carry out general broken operation more than the working fluid pressure values (being predetermined) according to running state.
(8) stop the L side of changing valve 4b solenoidal excitatory, with supply pipeline 4 sealing.At this moment, though working oil can be from pilot relief valve 3 natural leaks, because the effect of accumulator 4e, pilot pressure can continue to keep its pressure in longer time for example 10 minutes needed time of geometric ratio.
(9) solenoid that is installed in the 1st switch valve 2b among the main hydraulic line 2 is carried out excitatory,, main shaft 20 is risen to supply with working oil to oil hydraulic cylinder 10.
(10) when the pressure of working oil in the oil hydraulic cylinder 10 reaches certain pressure and detected by the 1st pressure transducer 2d, think that just disintegrator returns to general running state, stop operation the solenoidal excitatory and oil hydraulic pump 2a of the 1st switch valve 2b.
Disintegrator is generally in service shown in the above his-and-hers watches 1, and the object lesson when causing in the oil hydraulic cylinder 10 abnormal pressure taking place because of blocking foreign matter is illustrated, but is not limited to this general operation.For example, carrying out main shaft lifting when operation repeatedly as shown in Figure 3, also can carry out same substantially hydraulic control.And in service in gyratory crusher shown in Figure 3, disintegrator is activated, oil hydraulic pump is carried out drive electric motor under the control of timer, rotate and reverse repeatedly, that is make main shaft rise, descend, thus the raw material fragmentation that raw material feed device is supplied with.
That is to say, the oil hydraulic circuit 1 related according to this form of implementation 1, in the disintegrator running, when blocking things such as iron plate, on main shaft 20, act on excessive following thrust is arranged by cone part, pressure raises and when becoming too high in the oil hydraulic cylinder 10, by the 1st pressure transducer 2d to programming controller 30 incoming pressure checkout values.And it is excitatory to be installed in the release solenoid of the 2nd switch valve 5a among the pipeline 5 of pilot pressure by 30 pairs of programming controllers, and this switch valve 5a is opened.So pilot pressure is released to working oil fuel tank 8, the last thrust of the taper valve core 3b of pilot relief valve 3 diminishes and valve is opened.Therefore, working oil overflow and the pressure in the oil hydraulic cylinder 10 are reduced, thus can avoid excessive load to act on disintegrator.In addition, main shaft 20 descends and makes the width of exhaust port become big, thereby can be at an easy rate will cause that the excessive foreign matter of load discharges in crushing chamber.
In addition, when the 1st pressure transducer 2d detects pressure below the pressure set points, raise by the solenoidal excitatory pilot pressure that makes of the L side of changing valve 4b.Meanwhile, the solenoid of the 1st switch valve 2b is excitatory and supply with working oil till the pressure from the working oil of oil hydraulic pump 2a reaches set pressure to oil hydraulic cylinder 10, and disintegrator will return to the normal operating condition that blocks before the foreign matter.
According to this oil hydraulic circuit 1, thereby can make the working oil in the oil hydraulic cylinder 10 abnormal pressure in this oil hydraulic cylinder 10 be reduced, thereby needn't as existing gyratory crusher, in main hydraulic line 2, accumulator be set from pilot relief valve 3 overflows.Therefore, compared with prior art can be far for promptly reducing the abnormal pressure in the oil hydraulic cylinder.Its result needn't worry that the formation of its oil film of sliding bearing that the lower end surface of main shaft 20 is supported can be hindered, problem such as needn't worry can take place that this sliding bearing is burnt to death.Have again,, also can eliminate immediately and exceed the such overload state of design strength, therefore needn't worry that disintegrator integral body can sustain damage even in the great occasion of load that produces.
In addition owing in the main hydraulic line 2 accumulator is not set, because of the temperature difference and the variation of the oil hydraulic cylinder that the causes 10 interior working fluid pressures of passing in time less, therefore, the variation of main shaft holding power is little, the crusher in crushing performance can not change.And, needn't strengthen the caliber of main hydraulic line 2, thereby the oil mass of working oil is less in the main hydraulic line 2.Therefore, piston 11 unsettled phenomenons can not take place, can carry reliably because of carrying out the crushing force that fragmentation produces.Therefore, can make the particle size stable of broken goods, and can make the rock in the crushing chamber or the density of ore keep certain, thereby the crushing performance of gyratory crusher can not reduce, can make broken Products Quality keep certain level.
In addition, according to oil hydraulic circuit 1, the pressure occasion jumpy of working oil in material density increase, the oil hydraulic cylinder 10 in crushing chamber, not that the traction by oil hydraulic pump descends main shaft as the disintegrator that the public clear 56-36981 communique of aforementioned spy is put down in writing, but make the abnormal pressure in this oil hydraulic cylinder 10 to reduce rapidly from pilot relief valve 3 overflows by the working oil in the oil hydraulic cylinder 10.Therefore, the pressure of working oil can not raise in the oil hydraulic cylinder 10, can not be the packing state in the crushing chamber, and therefore, disintegrator can not take place has the phenomenon of shutting down under the situation of raw material in filling, can stably work continuously.
Secondly, the controlling method to oil hydraulic circuit of the present invention describes in conjunction with Fig. 4.This form of implementation is the pilot pressure supply mean of pilot pressure supply pipeline with the difference of form of implementation 1.In addition formation is identical, therefore, gives identical numbering to identical part, describes with regard to difference.
As the oil hydraulic circuit 1 of this form of implementation (below be called form of implementation 2), 1 related Fig. 1 compares as can be known from Fig. 4 and form of implementation, constitutes to supply with pilot pressures by oil hydraulic pump 4a to pilot pressure supply pipeline 4.
Therefore, the oil hydraulic circuit 1 related according to this form of implementation 2, same control in the time of can carrying out with form of implementation 1, thereby have equal effect.But owing in main hydraulic line 2 and pilot pressure supply pipeline 4, have oil hydraulic pump respectively, therefore, with an oil hydraulic pump to pipeline 2 and pipeline 4 the two form of implementation 1 of supplying with working oil compare, it is simple that control is wanted.In addition, boosting after working fluid pressures reduce in the oil hydraulic cylinder 10, can with supply with working oil to oil hydraulic cylinder 10 and carry out abreast.Therefore, can accelerate the resume speed after the emergency overflow, shorten performance and reduce the time, therefore, the effect of the broken production of articles efficient that can be improved.
By above explanation as can be known, controlling method according to oil hydraulic circuit and this oil hydraulic circuit of gyratory crusher of the present invention, be by from the pilot relief valve overflow abnormal pressure in this oil hydraulic cylinder being reduced the working oil in the oil hydraulic cylinder, therefore, need in main hydraulic line, accumulator be set, compare with the invention that aforementioned communique is put down in writing, can be far for the abnormal pressure in the oil hydraulic cylinder be reduced.Therefore, needn't worry that the formation of its oil film of sliding bearing that the lower end surface of main shaft is supported can be hindered, problem such as needn't worry can take place that this sliding bearing is burnt to death.Have again,, also can eliminate immediately and exceed the such overload state of design strength, therefore, needn't worry that gyratory crusher integral body can sustain damage even in the great occasion of load that produces.
In addition, as mentioned above, in the main hydraulic line accumulator is not set, in the oil hydraulic cylinder that takes place because of the passage of the temperature difference or time the variation of the pressure of working oil less, therefore, the variation of the gyratory crusher crushing performance that the variation of main shaft holding power causes is less.Have again, do not need to make the oil mass of working oil in winner's hydraulic line less, thereby the unsettled phenomenon of piston can not take place, can carry reliably because of carrying out the crushing force that fragmentation produces for guaranteeing that responsiveness increases the caliber of main hydraulic line.Therefore, can make the density of interior rock of crushing chamber or ore keep certain, make the particle size stable of broken goods.That is, stable by the crushing performance that makes gyratory crusher, can make broken Products Quality keep certain level.
Have again, the pressure occasion jumpy of working oil in material density increase in crushing chamber, the oil hydraulic cylinder, not that the traction by oil hydraulic pump descends main shaft as the gyratory crusher that aforementioned patent document 2 is put down in writing, but pass through the interior working oil of oil hydraulic cylinder from the pilot relief valve overflow, make what the interior abnormal pressure of oil hydraulic cylinder reduced rapidly.Therefore, different with the disintegrator of the public clear 56-36981 communique record of aforementioned spy, the pressure of working oil can not raise in the oil hydraulic cylinder; can not be the packing state in the crushing chamber; therefore, gyratory crusher can not shut down under filling has the situation of raw material, can stably carry out operation continuously.
Though described the present invention according to preferred embodiments and drawings, under the prerequisite that does not depart from the claim scope, can do various equivalents or replacement.
Claims (4)
1. the oil hydraulic circuit of a gyratory crusher, to supporting and can freely adjust the oil hydraulic cylinder supply working oil of its upper-lower position with the main shaft of the cycle of cone part and can make the pressure of working oil in the oil hydraulic cylinder keep certain to having fragmentation, it is characterized in that said oil hydraulic circuit also has:
Supply with the oil hydraulic pump of working oil to said oil hydraulic circuit;
The main hydraulic line that to supply with to said oil hydraulic cylinder from the working oil that said oil hydraulic pump extrudes, said oil hydraulic pump is not communicated with via accumulator with oil hydraulic cylinder;
Make the pilot relief valve of the working oil overflow in the said oil hydraulic cylinder by the pilot pressure of releasing;
Supply with the pilot pressure supply pipeline of pilot pressure to said pilot relief valve; And,
The pilot pressure of pilot pressure of said pilot pressure supply pipeline of the releasing pipeline of releasing.
2. as the oil hydraulic circuit of the said gyratory crusher of claim 1, it is characterized in that, also have
The oil hydraulic pump that is provided with in addition with respect to said oil hydraulic pump, be used for supplying with working oil to said pilot pressure supply pipeline.
3. the controlling method of the oil hydraulic circuit of a gyratory crusher is characterized in that, said controlling method comprises:
Pressure to working oil in the said main hydraulic line of the said oil hydraulic circuit of claim 1 detects with pressure transducer;
To controlling to the pressure of the working oil of said oil hydraulic cylinder supply, make the detected pressure of said pressure transducer in set scope by said main hydraulic line;
When the pressure of the detected working oil of said pressure transducer surpassed set value, the pilot pressure supplied with to pilot relief valve of releasing was to discharge the working oil in the said oil hydraulic cylinder; And,
When by the working oil of discharging in the said oil hydraulic cylinder, the pressure recovery of the detected working oil of said pressure transducer when following, returns to set value with said pilot pressure to set value.
4. the controlling method of the oil hydraulic circuit of a gyratory crusher, with main hydraulic line can freely adjust the oil hydraulic cylinder supply working oil of its upper-lower position to the main shaft with broken cycle with cone part is supported and to said oil hydraulic cylinder in the pressure and the oil mass of working oil control, it is characterized in that said controlling method comprises:
Pressure to working oil in the said main hydraulic line detects with pressure transducer;
To controlling to the pressure of the working oil of said oil hydraulic cylinder supply without accumulator, make the detected pressure of said pressure transducer in set scope by said main hydraulic line; And,
When the pressure of the detected working oil of said pressure transducer surpasses predefined set value, release the pilot pressure supplied with to pilot relief valve to discharge the working oil in the said oil hydraulic cylinder, when having evaded abnormal pressure by the discharging working oil, make said pilot pressure return to set pressure, make the pressure of working oil in the said oil hydraulic cylinder automatically restore to set pressure.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2002310477A JP3962670B2 (en) | 2002-10-25 | 2002-10-25 | Hydraulic circuit of a rotary crusher and control method of the hydraulic circuit |
| JP310477/02 | 2002-10-25 | ||
| JP310477/2002 | 2002-10-25 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1515800A true CN1515800A (en) | 2004-07-28 |
| CN1299012C CN1299012C (en) | 2007-02-07 |
Family
ID=32455958
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2003101043326A Expired - Fee Related CN1299012C (en) | 2002-10-25 | 2003-10-24 | Hydraulic circuit and control method for rotary breaker |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP3962670B2 (en) |
| CN (1) | CN1299012C (en) |
| AU (1) | AU2003255181A1 (en) |
| ZA (1) | ZA200308165B (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102235174A (en) * | 2010-04-16 | 2011-11-09 | S.A.阿姆斯特朗有限公司 | Improvements in and relating to long wall hydraulic supply systems |
| CN102310010A (en) * | 2011-10-02 | 2012-01-11 | 长兴县长虹路桥矿山机械设备有限公司 | Hard protection and cavity clearing means for multi-cylinder hydraulic rolling cone crusher |
| CN102357371A (en) * | 2011-10-02 | 2012-02-22 | 长兴县长虹路桥矿山机械设备有限公司 | Multi-cylinder hydraulic antifriction bearing taper crusher |
| CN104747540A (en) * | 2015-03-17 | 2015-07-01 | 辽宁新隆基液压润滑机械有限公司 | Hydraulic system for cone crusher |
| CN104870095A (en) * | 2012-10-26 | 2015-08-26 | 蒂森克虏伯工业解决方案股份公司 | Gyratory crusher for comminuting material to be crushed |
| CN105545847A (en) * | 2016-02-26 | 2016-05-04 | 华侨大学 | Hydraulic control system of crusher |
| 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 |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101543797B (en) * | 2009-04-29 | 2010-10-13 | 宝钢工程技术集团有限公司 | Vertical roller mill hydraulic system |
| SE535213C2 (en) * | 2010-12-20 | 2012-05-22 | Sandvik Intellectual Property | Hydraulic circuit and method for controlling a gyratory cone crusher |
| CN103394391B (en) * | 2013-07-20 | 2015-10-28 | 长兴山润机械有限公司 | A kind of hydraulic system of roll crusher |
| JP6544764B2 (en) * | 2014-12-26 | 2019-07-17 | 株式会社テクノリンクス | Crusher |
| CN106807481A (en) * | 2015-11-30 | 2017-06-09 | 成都九十度工业产品设计有限公司 | A kind of gyratory crusher |
| JP7010763B2 (en) * | 2018-05-21 | 2022-01-26 | 株式会社アーステクニカ | Control device and method for rotary crusher and rotary crusher |
| CN112780620A (en) * | 2021-01-19 | 2021-05-11 | 浙江中液机械设备有限公司 | Hydraulic system, lubricating system and cone crusher |
| CN113102089A (en) * | 2021-05-07 | 2021-07-13 | 徐州徐工矿业机械有限公司 | Automatic wear compensation system for liner plate of cone crusher and control method |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5048292A (en) * | 1990-08-02 | 1991-09-17 | Kubik Philip A | Dual pump traverse and feed system |
| DE4128656C2 (en) * | 1991-08-29 | 1994-10-20 | Bosch Gmbh Robert | Hydraulic actuating device and its use |
| DE19535677A1 (en) * | 1995-09-26 | 1997-03-27 | Bosch Gmbh Robert | Device for controlling a hydraulic motor |
| JPH10272375A (en) * | 1997-03-31 | 1998-10-13 | Kurimoto Ltd | Method for controlling gyratory crusher |
| AT411784B (en) * | 2000-05-03 | 2004-05-25 | Weber Walter | CONTROL DEVICE FOR DOUBLE-ACTING HYDRAULIC WORKING CYLINDERS |
-
2002
- 2002-10-25 JP JP2002310477A patent/JP3962670B2/en not_active Expired - Fee Related
-
2003
- 2003-01-01 ZA ZA200308165A patent/ZA200308165B/en unknown
- 2003-10-17 AU AU2003255181A patent/AU2003255181A1/en not_active Abandoned
- 2003-10-24 CN CNB2003101043326A patent/CN1299012C/en not_active Expired - Fee Related
Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102235174A (en) * | 2010-04-16 | 2011-11-09 | S.A.阿姆斯特朗有限公司 | Improvements in and relating to long wall hydraulic supply systems |
| CN102235174B (en) * | 2010-04-16 | 2015-11-25 | S.A.阿姆斯特朗有限公司 | Longwell fluid pressure supply system and relevant improvement thereof |
| CN102310010A (en) * | 2011-10-02 | 2012-01-11 | 长兴县长虹路桥矿山机械设备有限公司 | Hard protection and cavity clearing means for multi-cylinder hydraulic rolling cone crusher |
| CN102357371A (en) * | 2011-10-02 | 2012-02-22 | 长兴县长虹路桥矿山机械设备有限公司 | Multi-cylinder hydraulic antifriction bearing taper crusher |
| CN102310010B (en) * | 2011-10-02 | 2012-08-22 | 长兴县长虹路桥矿山机械设备有限公司 | Hard protection and cavity clearing means for multi-cylinder hydraulic rolling cone crusher |
| CN102357371B (en) * | 2011-10-02 | 2013-07-31 | 长兴县长虹路桥矿山机械设备有限公司 | Multi-cylinder hydraulic antifriction bearing taper crusher |
| CN104870095A (en) * | 2012-10-26 | 2015-08-26 | 蒂森克虏伯工业解决方案股份公司 | Gyratory crusher for comminuting material to be crushed |
| CN104870095B (en) * | 2012-10-26 | 2017-03-15 | 蒂森克虏伯工业解决方案股份公司 | Gyratory crushers for crushing materials to be crushed |
| US10335795B2 (en) | 2012-10-26 | 2019-07-02 | Thyssenkrupp Industrial Solutions Ag | Gyratory crusher for comminuting material to be crushed |
| CN104747540A (en) * | 2015-03-17 | 2015-07-01 | 辽宁新隆基液压润滑机械有限公司 | Hydraulic system for cone crusher |
| CN105545847A (en) * | 2016-02-26 | 2016-05-04 | 华侨大学 | Hydraulic control system of crusher |
| CN105545847B (en) * | 2016-02-26 | 2017-07-21 | 华侨大学 | crusher hydraulic control 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 |
Also Published As
| Publication number | Publication date |
|---|---|
| ZA200308165B (en) | 2004-06-25 |
| JP3962670B2 (en) | 2007-08-22 |
| JP2004141780A (en) | 2004-05-20 |
| AU2003255181A1 (en) | 2004-05-13 |
| CN1299012C (en) | 2007-02-07 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN1515800A (en) | Hydraulic circuit and control method for rotary breaker | |
| RU2649619C1 (en) | Method of hydraulic testing and device for hydraulic testing | |
| CN102489650B (en) | Automatic liquid supplementing and draining system with liquid filling tank | |
| US5783983A (en) | Internal mixer | |
| KR20150007342A (en) | Method and device for adaptively controlling a hydraulic press | |
| US8753034B2 (en) | Auxiliary pressure relief reservoir for crash barrier | |
| CN104588198A (en) | Full-automatic control method for rolling type flat cone roll crusher | |
| CN1298606C (en) | Hydraulic lift comprising a pressure accumulator and method for controlling and regulating one such lift | |
| US6981665B2 (en) | Cone crusher bowl adjustment mechanism | |
| KR101217755B1 (en) | Hydraulic control arrangement | |
| CN207680772U (en) | Cone crusher discharge gate control system and cone crusher | |
| CN114160242B (en) | Large double-cavity multi-cylinder cone crusher and starting-up adjusting method | |
| CN103660061B (en) | Banbury hydraulic control device | |
| JP6127466B2 (en) | Vertical roller mill | |
| CN113083440B (en) | Control method of high-pressure roller mill roller gap dynamic control and deviation correction hydraulic system | |
| CN203214496U (en) | Potential energy recycling hydraulic control system of lifting equipment | |
| CN103672057A (en) | High-pressure safety rapid shut off valve | |
| CN102556153B (en) | Steering hydraulic drive system for vehicle | |
| CN203214495U (en) | Potential energy recycling hydraulic control system of lifting equipment | |
| RU2393091C2 (en) | Hydraulic press | |
| KR101134007B1 (en) | Hydraulic cylinder pressure control device of brake pad makingmachine | |
| JP2011147948A (en) | Hydraulic press, and method for controlling hydraulic press | |
| CN223676637U (en) | Hydraulic control valve for multi-cylinder cone crusher | |
| CN206592362U (en) | A kind of screw thread inserting type Fill valve | |
| CN204878132U (en) | Hydro -cylinder smooth starting and pressure relief device are expected with pressing to gate -type scrap shearing machine cylinder for shear |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20070207 Termination date: 20201024 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |