CN101793272A - Hydraulic circuit for construction machinery - Google Patents
Hydraulic circuit for construction machinery Download PDFInfo
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- CN101793272A CN101793272A CN200910261066A CN200910261066A CN101793272A CN 101793272 A CN101793272 A CN 101793272A CN 200910261066 A CN200910261066 A CN 200910261066A CN 200910261066 A CN200910261066 A CN 200910261066A CN 101793272 A CN101793272 A CN 101793272A
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- 238000010276 construction Methods 0.000 title abstract description 3
- 230000006835 compression Effects 0.000 claims abstract description 28
- 238000007906 compression Methods 0.000 claims abstract description 28
- 238000007599 discharging Methods 0.000 claims abstract description 14
- 238000000605 extraction Methods 0.000 claims description 41
- 230000002411 adverse Effects 0.000 claims description 11
- 230000007935 neutral effect Effects 0.000 claims description 11
- RLLPVAHGXHCWKJ-IEBWSBKVSA-N (3-phenoxyphenyl)methyl (1s,3s)-3-(2,2-dichloroethenyl)-2,2-dimethylcyclopropane-1-carboxylate Chemical compound CC1(C)[C@H](C=C(Cl)Cl)[C@@H]1C(=O)OCC1=CC=CC(OC=2C=CC=CC=2)=C1 RLLPVAHGXHCWKJ-IEBWSBKVSA-N 0.000 abstract 1
- 238000006243 chemical reaction Methods 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 230000007704 transition Effects 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000009987 spinning Methods 0.000 description 2
- 239000002131 composite material Substances 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2264—Arrangements or adaptations of elements for hydraulic drives
- E02F9/2267—Valves or distributors
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2278—Hydraulic circuits
- E02F9/2292—Systems with two or more pumps
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
- B60Y2200/00—Type of vehicle
- B60Y2200/40—Special vehicles
- B60Y2200/41—Construction vehicles, e.g. graders, excavators
- B60Y2200/412—Excavators
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- Engineering & Computer Science (AREA)
- Mining & Mineral Resources (AREA)
- Civil Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structural Engineering (AREA)
- Fluid-Pressure Circuits (AREA)
- Operation Control Of Excavators (AREA)
Abstract
The inventive hydraulic circuit for construction machinery includes: a walking straight advancing valve (190), having first to third positions and a compression part applied with signal pressure, and switching in the scope from the first to the third positions based on the size of the signal pressure applied to the compression part; and a rotary parallel pipeline (172), making the working oil of the third pump outflank the walking straight advancing valve to supply to a rotary control valve. If the walking straight advancing valve is switched to the first position, the third pump is communicated with the oil discharging pipeline at a first opening value, the connection between the third pump to the first and second merging pipelines is cut off; if the walking straight advancing valve is switched to the second position, the third pump is communicated to the first merging pipeline (196), the third pump is communicated to the second merging pipeline (197), and the third pump is communicated with the oil discharging pipeline at a second opening value smaller than the first opening value; if the walking straight advancing valve is switched to the third position, the third pump is communicated to the first and second merging pipelines, and the connection between the third pump and the oil discharging pipeline is cut off.
Description
Technical field
The present invention relates to as engineering machinery such as excavators, relate in particular to when carrying out composite move such as forward position (front) operation, walking and rotation simultaneously, can prevent because of whirl then the oil hydraulic circuit (hydraulic circuit for construction machinery) of the engineering machinery of the rotational impact that produces.
Background technique
In general,, make vehicle to run, make the upper rotating body rotation, forward position working machines such as cantilever, rocking arm and scraper bowl cylinder are driven by revolution motor as oil hydraulic motor by running motor as oil hydraulic motor as engineering machinery such as excavators.
So, each drive unit all drives by working oil, therefore need suitably distribute the working oil of discharging from pump to each drive unit.Especially, when carrying out walking and forward position operation or rotation simultaneously, left lateral is walked motor and right lateral is walked working oil underfed some in the motor if supply to, and then engineering machinery can not directly be advanced.In order to address this problem, to be provided with walking and directly to advance valve, to be used for supplying with sufficient flow to running motor.Fig. 1 a to Fig. 1 c shows an example of this oil hydraulic circuit.
With reference to Fig. 1 a, walking is directly advanced valve 30 under original state, first gear pump 10 is connected with oil extraction pipeline 40 and discharge from the working oil of first gear pump 10 discharges, and first gear pump 10 is collaborated pipeline 41,42 cut-outs from first and second.And the front end that the circuitous walking of the working oil of first gear pump 10 is directly advanced valve 30 and arrived rotary control valve 50 by the parallel pipeline 43 of the rotation that is connected rotary control valve 50 is in holding state.
Under this state, if produce walk signal and rocking arm operation signal, then the first walking control valve 60 and rocking arm one fast control valve 70 are converted to the state shown in Fig. 1 b.So first of the conversion walking control valve 60 cuts off first and second branch signal pipeline 32,33 that is connected with second gear pump 20 with rocking arm one fast control valve 70.So, on the straight inlet signal pipeline 31 of walking of the compression zone 30a that connects the valve 30 of walking directly to advance and second gear pump 20, form high pressure.Thereby walking is directly advanced valve 30 and is converted to state shown in Fig. 1 b.
Be converted to state shown in Fig. 1 b if valve 30 is directly advanced in walking, then first gear pump 10 directly advances valve 30 and collaborates pipeline 41,42 with first and second and be connected by walking.In view of the above, the working oil of discharging from first gear pump 10 is fed into cantilever one fast control valve 90 by the first interflow pipeline 41, and is fed into rocking arm one fast control valve 70 by the second interflow pipeline 42.In addition, supply with working oil by main pump P1 to the first walking control valve 60.
In addition, described first and second interflow pipeline 41,42 directly advances parallel pipeline 43 connections with rotation of valve 30 by walking.And the working oil that flows by described first and second interflow pipeline 41,42 is confluxed at cantilever one fast control valve 90 and the front end of rocking arm one fast control valve 70 and the working oil of main pump P1, P2.At this, the working pressure of cantilever and rocking arm is about 100bar.Therefore, on described first and second interflow pipeline 41,42, form the pressure about 100bar, and directly advance valve 30 cut-outs, so also produce pressure about 100bar rotating parallel pipeline 43 because the parallel pipeline 43 of described rotation is communicated with described first and second interflow pipeline 41,42 and oil extraction pipeline 40 is walked.In addition, rotary work pressure is about 50bar.Therefore, for rotate drive and with rotary control valve 50 from the state exchange shown in Fig. 1 b to the left side or during the right side, the working oil of the high pressure high flow capacity about 100bar supplies to revolution motor 51 by rotary control valve 50.In view of the above, revolution motor 51 is sharply driven and is made the unexpected fast rotational of upper rotating body.This phenomenon also is referred to as rotational impact.When producing this rotational impact and since upper rotating body with the intention that is different from the manipulator fast rotational suddenly, the possibility that therefore security incident takes place is very high.
In addition, when walking simultaneously and forward position operation and rotation when driving, because the working pressure of described cantilever and rocking arm is relatively large, therefore the major part of the working oil of discharging from first gear pump 10 will supply to revolution motor 51.That is it is few, to supply to the working oil of cantilever cylinder and rocking arm cylinder by first and second interflow pipeline 41,42.Owing to this reason, the actuating speed of forward position working machine significantly reduces, thereby working efficiency descends.
Especially, except cantilever, also can load the weight of rocking arm and scraper bowl on the cantilever cylinder, therefore at the indoor generation high pressure of the rising of cantilever cylinder.And then, when the second walking control valve (not shown) is only changed half left and right sides, the part of the working oil of main pump P1 supplies to running motor by walking control valve (not shown), and the residue working oil of main pump supplies to the cantilever cylinder by cantilever one fast control valve 90.But, because the working oil of described main pump is confluxed at the front end and the first interflow pipeline 41 of cantilever one fast control valve 90, and producing on the described first interflow pipeline 41 only is the working pressure of the described revolution motor 51 about 50bar, therefore have only pressure when working oil to reach 100bar when above, the working oil that supplies to the cantilever cylinder is directly advanced valve 30 to rotating parallel pipeline 43 adverse currents by described first interflow pipeline 41 and walking.And then, the working oil of the bigger flow of supply on described revolution motor 51, so not only rotational impact becomes bigger, and the actuating speed of cantilever cylinder can obviously reduce.
Therefore in addition, the compression zone 30a that valve 30 is directly advanced in described walking is communicated with second gear pump 20, when walking control valve 60 and forward position control valve 70 are changed simultaneously, walks and directly advances valve 30 and be transformed into state shown in Fig. 1 b suddenly from as shown in Figure 1a state.That is, walking is directly advanced valve 30 and is changed in the mode of opening/close (ON/OFF).Because walking is directly advanced valve and is changed in the mode of opening/closing, thus oil extraction pipeline 40 can be cut off suddenly, thereby form very big pressure suddenly at the parallel pipeline 43 of described rotation.This factor can strengthen described rotational impact.Unaccounted symbol 80 is the cantilever two-speed control valves that are used to control selection device.
Summary of the invention
The present invention makes in order to address the above problem, and its purpose is to provide a kind of not only can prevent rotational impact, but also can prevent the oil hydraulic circuit of the engineering machinery that the actuating speed of forward position working machine when multiple working descends.
In order to achieve the above object, oil hydraulic circuit according to engineering machinery of the present invention is applicable to following engineering machinery, this project machinery comprises: the first pump P1 is used for supplying with working oil to first running motor 101 and the first forward position working machine 112,121 respectively by the first walking control valve 100 and the first forward position control valve 110,120 respectively; The second pump P2 is used for supplying with working oil to second running motor 141 and the second forward position working machine 151 respectively by the second walking control valve 140 and the second forward position control valve 150 respectively; The 3rd pump P3 is used for supplying with working oil by rotary control valve 170 to revolution motor 171; The first interflow pipeline 196 at the front end of the described first forward position control valve 110,120, makes from the working oil of described the 3rd pump P3 discharge and the work oil phase of the described first pump P1 and confluxes; The second interflow pipeline 197 is used for the front end at the described second forward position control valve 150, and the working oil of described the 3rd pump P3 and the work oil phase of the described second pump P2 are confluxed; And oil extraction pipeline 195, be used for the working oil of described the 3rd pump P3 is discharged by described rotary control valve 170; The oil hydraulic circuit of described engineering machinery comprises: valve 190 is directly advanced in walking, the compression zone 190a that has first to the 3rd position 191,192,193 and be applied in signal pressure Pa4, Pb4, Pa5, Pb5, and, in the scope of described first to the 3rd position 191,192,193, change according to the size of the signal pressure Pa4, the Pb4 that are applied to described compression zone 190a, Pa5, Pb5; And rotate parallel pipeline 172, make the circuitous described walking of working oil of described the 3rd pump P3 directly advance valve 190 and supply to described rotary control valve 170; Wherein, if described walking is directly advanced valve 190 and is transformed into described primary importance 191, then described the 3rd pump P3 is communicated with the first aperture amount with described oil extraction pipeline 195, and described the 3rd pump P3 and described first and second interflow pipeline 196,197 connection is cut off, if described walking is directly advanced valve 190 and is transformed into the described second place 192, then described the 3rd pump P3 is communicated with the described first interflow pipeline 196 by the first stream 192a, described the 3rd pump P3 is communicated with the described second interflow pipeline 197 by the second stream 192b, described the 3rd pump P3 is communicated with described oil extraction pipeline 195 with the second aperture amount less than the first aperture amount by the 3rd stream 192c, if described walking is directly advanced valve 190 and is transformed into described the 3rd position 193, then described the 3rd pump P3 collaborates pipeline 196 with described first and second respectively, 197 are communicated with, and described the 3rd pump P3 was cut off with being connected of described oil extraction pipeline 195.
According to one embodiment of the invention, the oil hydraulic circuit of described engineering machinery also comprises: shuttle valve unit 194, and the big signal pressure of walk signal pressure Pa 4, Pb4, Pa5, Pb5 that is used for putting on described first and second walking control valve 100,140 is applied to the compression zone 190a that valve 190 is directly advanced in described walking; The straight inlet signal pipeline 103 of walking is used to connect the compression zone 190a that valve 190 is directly advanced in described shuttle valve unit 194 and described walking; The first branch signal pipeline 103a, 103 branches come out from the straight inlet signal pipeline of described walking, and are connected to described oil extraction pipeline by described first and second walking control valve 100,140 successively; And the second branch signal pipeline 103b, be connected to the oil extraction pipeline by described first and second forward position control valve 110,120,150 respectively; Wherein, in converting described first and second walking control valve 100,140 at least one breaks away from neutral condition, and when at least one in described first and second forward position control valve 110,120,150 broke away from neutral condition, described first and second branch signal pipeline 103a, 103b and oil extraction pipeline were tangent disconnected.
And, the oil hydraulic circuit of described engineering machinery can also comprise that being located at described the 3rd pump P3 and described walking directly advances one-way valve 198 between the valve 190, collaborates pipeline 196 adverse currents to the parallel pipeline 172 of described rotation to be used to prevent the working oil from the described first pump P1 discharges by described first.
In addition, in order to achieve the above object, the oil hydraulic circuit of engineering machinery of the present invention is applicable to following engineering machinery, this project machinery comprises: the first pump P1, to be used for supplying with working oil to first running motor 101 and the first forward position working machine 112,121 respectively by the first walking control valve 100 and the first forward position control valve 110,120 respectively; The second pump P2 is to be used for supplying with working oil to second running motor 141 and the second forward position working machine 151 respectively by the second walking control valve 140 and the second forward position control valve 150 respectively; The 3rd pump P3 is to be used for supplying with working oil by rotary control valve 170 to revolution motor 171; The first interflow pipeline 196 to be used for the front end at the described first forward position control valve 110,120, to make from the working oil of described the 3rd pump P3 discharge and the work oil phase of the described first pump P1 and confluxes; The second interflow pipeline 197 to be used for the front end at the described second forward position working machine 151, confluxes the working oil of described the 3rd pump P3 and the work oil phase of the described second pump P2; And oil extraction pipeline 195, to be used for that the working oil of described the 3rd pump P3 is passed through described rotary control valve 170 dischargings, the oil hydraulic circuit of described engineering machinery is characterised in that, has the compression zone 290a that is applied in signal pressure Pa4, Pb4, Pa5, Pb5, and comprise: valve 290 is directly advanced in walking, according to the size of the signal pressure Pa4, the Pb4 that are applied to described compression zone 290a, Pa5, Pb5, between the 4th position 291 and the 5th position 292, change; Rotate parallel pipeline 172, directly advance valve 290 and described the 3rd pump P3 is connected with described rotary control valve 170 to be used for circuitous described walking; And shuttle valve unit 194, be applied to the compression zone 290a that valve 290 is directly advanced in described walking with the big signal pressure of walk signal pressure Pa 4, Pb4, Pa5, Pb5 that is used for putting on described first and second walking control valve 100,140; Wherein, if described walking is directly advanced valve 290 and is transformed into described the 4th position 291, then described the 3rd pump P3 is communicated with described oil extraction pipeline 195, and described the 3rd pump P3 is cut off with described first and second interflow being connected of pipeline 196,197, if described walking is directly advanced valve 290 and is transformed into described the 5th position 292, then described the 3rd pump P3 is communicated with described first and second interflow pipeline 196,197 respectively, and described the 3rd pump P3 was cut off with being connected of described oil extraction pipeline 195.
According to aforesaid technological scheme, directly advance valve in walking the second place is set, make first and second interflow pipeline is connected with the 3rd pump, simultaneously the oil extraction pipeline is connected to the 3rd pump, thereby when carrying out forward position operation and walking and spinning movement simultaneously, the 3rd pump can prevent the rotational impact that is produced by sudden spinning movement in view of the above by rotating flow and the pressure that parallel pipeline and rotary control valve reduce the working oil that supplies to revolution motor.
And, apply walk signal pressure by the compression zone that directly advances valve to walking, can directly advance the variable quantity of valve according to the operation amount linearity control walking of walking operation unit, can prevent to supply with suddenly the working oil of high pressure high flow capacity by rotating parallel pipeline and rotary control valve thus, thereby can thoroughly prevent rotational impact to revolution motor.
And, directly advance one-way valve is set between the valve at the 3rd pump and walking, thereby the working oil that can prevent first pump is directly advanced the valve adverse current to the parallel pipeline of rotation by the described first interflow pipeline with walking, rotational impact not only can be relaxed more thus, but also the actuating speed of forward position working machine can be improved.
Description of drawings
Fig. 1 a and Fig. 1 b are the figure that existing engineering machinery hydraulic loop probably is shown.
Fig. 2 probably illustrates the figure of the oil hydraulic circuit of engineering machinery according to an embodiment of the invention.
Fig. 3 a to Fig. 3 c is the figure of working procedure that is used to illustrate the oil hydraulic circuit of engineering machinery shown in Figure 2.
Fig. 4 is the figure that the oil hydraulic circuit of other embodiment's engineering machinery according to the present invention probably is shown.
Among the figure:
P1, P2, P3-first to the 3rd pump 100-first walking control valve
110-cantilever one fast control valve 120-scraper bowl control valve
The 140-second walking control valve 150-rocking arm one fast control valve
170-rotary control valve 172-rotates parallel pipeline
The compression zone that valve is directly advanced in valve 190a-walking is directly advanced in the 190-walking
191,192,193-first to the 3rd position 192a, 192b, 192c-first to the 3rd stream
The 196-first interflow pipeline 197-second interflow pipeline
The 198-one-way valve
Embodiment
Below, describe oil hydraulic circuit in detail according to the engineering machinery of the embodiment of the invention.
With reference to Fig. 2, the oil hydraulic circuit of engineering machinery when carrying out the rotation of forward position operation and walking and upper rotating body simultaneously, can prevent the upper rotating body rotational impact phenomenon of rotation suddenly according to an embodiment of the invention.The oil hydraulic circuit of this engineering machinery comprises that walking directly advances valve 190, shuttle valve unit (shuttlevalve unit) 194 and the parallel pipeline 172 of rotation.
The working machine of using the engineering machinery of present embodiment drives according to the working oil that from first to the 3rd pump P1, P2, P3 discharge.
Specifically, the described first pump P1 supplies with working oil to first running motor 101, cantilever cylinder 112, scraper bowl cylinder 121 and rocking arm cylinder 151 respectively respectively by the first walking control valve 100, cantilever one fast control valve 110, scraper bowl control valve 120 and rocking arm two-speed control valve 130.The working oil of being supplied with by described rocking arm two-speed control valve 130 is confluxed with the working oil of discharging from the second pump P2 by means of not shown interflow pipeline and is supplied to rocking arm cylinder 151.But, when the described first walking control valve, 100 disengaging neutral conditions are transformed into a side or opposite side fully, the working oil of the described first pump P1 is cut off by the described first walking control valve 100 and can't be flow to each control valve 110,120,130, therefore supplies to first running motor 101 by described first 100 of the control valves of walking.Under this state, described walking is directly advanced valve 190 and is changed, and the working oil of described the 3rd pump P3 supplies to cantilever one fast control valve 110, scraper bowl control valve 120 and rocking arm two-speed control valve 130 by the first interflow pipeline 196.Below, will describe this working procedure in detail.At this, cantilever one fast control valve 110 and scraper bowl control valve 120 are defined as the first forward position control valve 110,120, cantilever cylinder 112 and scraper bowl cylinder 121 are defined as the first forward position working machine 112,121.
The described second pump P2 supplies with working oil to second running motor 141, rocking arm cylinder 151 and cantilever cylinder 112 respectively by the second walking control valve 140, rocking arm one fast control valve 150 and cantilever two-speed control valve 160 respectively.The working oil of being supplied with by described cantilever two-speed control valve 160 is confluxed with the working oil of discharging from the first pump P1 by means of not shown interflow pipeline and is supplied to cantilever cylinder 112.If be connected with the Appendage Task device as fixture and so on, then cantilever two-speed control valve 160 also plays the effect to this Appendage Task unit feeding working oil.But, when being transformed into a side or opposite side fully when the described second walking control valve, 140 disengaging neutral conditions, the working oil of the second pump P2 is cut off by the described second walking control valve 140 and can't be flow to described each control valve 150,160, therefore supplies to second running motor 141 by described second 140 of the control valves of walking.Under this state, described walking is directly advanced valve 190 and is changed, thereby the working oil of described the 3rd pump P3 supplies to cantilever two-speed control valve 160 and rocking arm one fast control valve 150 by the second interflow pipeline 197.At this, described rocking arm one fast control valve 150 is defined as the second forward position control valve 150, rocking arm cylinder 151 is defined as the second forward position working machine 151.
Described the 3rd pump P3 is by rotating parallel pipeline 172 and the parallel pipeline 182 of bulldozing is supplied with working oil to described rotary control valve 170 and soil-shifting control valve 180.But if some the changing in described first and second walking control valve 100,140, then described the 3rd pump P3 supplies with working oil by first and second interflow pipeline 196,197 to first and second forward position control valve 110,120,150 as previously mentioned.
As previously mentioned, when the input walk signal, owing to be cut off to described first and second pump P1 of described first and second forward position control valve 110,120,150 supplies, the working oil of P2, therefore described walking is directly advanced valve 190 conversion streams and is made the working oil of the 3rd pump P3 supply to described first and second forward position control valve 110,120,150.This walking is directly advanced valve 190 and is had compression zone 190a, and has first to the 3rd position 191,192,193 of changing according to the size that is applied to the signal pressure of described compression zone 190a.
Described primary importance 191 makes described the 3rd pump P3 be connected with oil extraction pipeline 195 with the first aperture amount, and cuts off being connected of described first and second interflow pipeline 196,197 and described the 3rd pump P3.This state directly advances the original state of valve 190, i.e. state of also not walking for walking.That is first and second walking control valve 100,140 is in the situation of neutral condition.Under this state, the working oil of discharging from the 3rd pump P3 is discharged along flow through rotary control valve 170 and soil-shifting control valve 180 of oil extraction pipeline 195.And the working oil of discharging from first and second pump P1, P2 supplies to first and second forward position control valve 110,120,150.
The described second place 192 is that described walking is directly advanced valve 190 and is transformed into crossover position before the 3rd position 193.On the described second place 192, be formed with: the first stream 192a that described the 3rd pump P3 is communicated to the described first interflow pipeline 196; Described the 3rd pump P3 is communicated to the second stream 192b of the described second interflow pipeline 197; And the 3rd stream 192c that the working oil of described the 3rd pump P3 is communicated to oil extraction pipeline 195.Described the 3rd stream 192c is to be discharged into oil extraction pipeline 195 less than the second aperture amount of the first aperture amount with the working oil of the 3rd pump P3.And then the working oil flow of the 3rd pump P3 that is discharged into described oil extraction pipeline 195 by described the 3rd stream 192c is less than the working oil flow that is discharged into the 3rd pump P3 of oil extraction pipeline 195 in described primary importance 191.So, by forming the 3rd stream 192c the part of the working oil of the 3rd pump P3 is discharged into oil extraction pipeline 195, thereby can reduce by rotating flow and the pressure that parallel pipeline 172 and rotary control valve 170 supply to the working oil of revolution motor 171, can prevent the phenomenon that revolution motor 171 drives suddenly in view of the above.That is, can prevent rotational impact.
Described the 3rd position 193 makes described the 3rd pump P3 be communicated with described first and second interflow pipeline 196,197 respectively, and cuts off being connected of described the 3rd pump P3 and described oil extraction pipeline 195.
In addition, the front end that directly advances valve 190 in described walking is provided with one-way valve 198.Described one-way valve 198 is used for when described walking is directly advanced valve 190 and is transformed into second and third position 192,193, prevent working oil by described first interflow pipeline 196 adverse currents to the parallel pipeline 172 of rotation.As follows by the described first interflow pipeline 196 to the situation that adverse current takes place the parallel pipeline 172 of described rotation.
When be not described first the walking control valve 100 change fully state the time, the part of the working oil of the first pump P1 supplies to described first running motor 101 by the described first walking control valve 100, and the remainder of the working oil of the described first pump P1 supplies to described cantilever one fast control valve 110 by cantilever one fast parallel pipeline 111.The pressure that the pressure of the working oil of described cantilever one fast parallel pipeline 111 is compared the parallel pipeline 172 of described rotation is high about 2 times.And then, if described cantilever one fast control valve 110 is converted to the disengaging neutral condition, the working oil that then flow into described cantilever one fast parallel pipeline 111 from described first pump P1 discharge is directly advanced valve 190 adverse currents to the parallel pipeline 172 of rotation by the described first interflow pipeline 196 with described walking.At this moment, the flow that supplies to the working oil of revolution motor 171 further increases, thereby not only makes described rotational impact further become big, and the actuating speed of described cantilever cylinder 112 will reduce.For preventing this situation, when described one-way valve 198 being located at walking directly advancing the front end of valve 190, can prevent aforesaid adverse current, this not only can guarantee the actuating speed of cantilever cylinder 112, and can also reduce rotational impact.
Described shuttle valve unit 194 is used for walk signal pressure Pa 4, Pb4, Pa5, Pb5 are applied to the compression zone 190a that valve 190 is directly advanced in described walking.This shuttle valve unit 194 will be applied to described compression zone 190a by maximum signal pressure Pa5 from signal pressure Pa4, the Pb4 of the output of walking operation unit 104, Pa5, Pb5.So, owing to walk signal pressure Pa 4, Pb4, Pa5, Pb5 are applied to the compression zone 190a that valve 190 is directly advanced in described walking, therefore can change and be applied to the size of signal pressure that the compression zone 190a of valve 190 is directly advanced in described walking according to the operation amount of described walking operation unit 104 by shuttle valve unit 194.And then, when the operation amount of walking operation unit 104 hour, it is less that the conversion amount that valve 190 changed from primary importance 191 is directly advanced in described walking, can reduce the amount that the working oil of the 3rd pump P3 is discharged by oil extraction pipeline 195 thus gradually.Therefore, the pressure of the working oil of the parallel pipeline 172 of described rotation increases gradually, thereby can prevent described revolution motor 171 unexpected driven phenomenons.
In addition, the signal pressure Pa5 of 194 outputs is applied to described compression zone 190a by the straight inlet signal pipeline 103 of walking from described shuttle valve unit.And the straight inlet signal pipeline 103 of described walking is branched to first and second branch signal pipeline 103a, 103b.The described first branch signal pipeline 103a is by forward position control valve 110,120,150,160, i.e. cantilever two-speed control valve 160, rocking arm one fast control valve 150, cantilever one fast control valve 110 and scraper bowl control valve 120 and be connected to the oil extraction pipeline.And the described second branch signal pipeline 103b is connected to the oil extraction pipeline by the second walking control valve 140 and the described first walking control valve 100 successively.Under this state, if the some control valves in the described forward position control valve 110,120,150 are converted to the disengaging neutral condition, and the some walking control valves in described first and second walking control valve 100,140 are converted to the disengaging neutral condition, then first and second branch signal pipeline 103a, 103b and oil extraction pipeline are tangent disconnected, and the pressure of the straight inlet signal pipeline 103 of described walking is risen.
Below, the working procedure of the oil hydraulic circuit of the engineering machinery of structure is elaborated to having as previously mentioned.
Fig. 3 a probably shows walking and directly advances the state that valve 190 is transformed into the second place 192.At first, operator is changed the second walking control valve 140, rocking arm one fast control valve 150 and rotary control valve 170 simultaneously.So the signal pressure Pa5 of described walking operation unit 104 is by 194 outputs of shuttle valve unit, and the signal pressure Pa5 of output is applied to the compression zone 190a that valve 190 is directly advanced in walking by the straight inlet signal pipeline 103 of walking.At this moment, described first and second branch signal pipeline 103a, 103b are in respectively by the rocking arm one fast control valve 150 and the second walking control valve 140 and the tangent disconnected state of oil extraction pipeline, and the signal pressure Pa5 that therefore results from walking operation unit 104 is applied to the compression zone 190a that valve 190 is directly advanced in described walking same as before.
If the compression zone 190a that directly advances valve 190 to walking applies signal pressure Pa5, then walking is directly advanced valve 190 and is transformed into the second place 192 from primary importance 191.So the 3rd pump P3 is communicated with first and second interflow pipeline 196,197 and oil extraction pipeline 195 respectively by first to the 3rd stream 192a, 192b, 192c respectively.
In addition, along with the described second walking control valve 140 is converted to state shown in Fig. 3 a, the working oil that the working oil of the described second pump P2 only supplies to second running motor, 141, the three pump P3 supplies to rocking arm cylinder 151 by the second interflow pipeline 197, rocking arm one fast parallel pipeline 152 and rocking arm one fast control valve 150 successively.
And the working oil of described the 3rd pump P3 supplies to revolution motor 171 by rotating parallel pipeline 172 and rotary control valve 170.At this moment, the working oil of discharging from described the 3rd pump P3 is discharged into oil extraction pipeline 195 by the 3rd stream 192c, and therefore described revolution motor 171 unexpected driven rotational impacts can not take place.
The transition status (being transformed into the state of the second place) of valve 190 is directly advanced in walking shown in Fig. 3 a, not only under the operation amount of described walking operation unit 104 and off-peak situation, take place, and under the operation amount of walking operation unit 104 reaches maximum situation, also can take place with transition state.Therefore, when being maximum, the operation amount of walking operation unit 104 also can prevent rotational impact.
Fig. 3 b probably shows when the operation amount of walking operation unit 104 reaches maximum, and valve 190 is transformed into the state of the 3rd position 193 through the second place 192 circuit diagram is directly advanced in walking.Under this state, described the 3rd pump P3 is in the state that cuts off with oil extraction pipeline 195, therefore can control the normal actuating speed of revolution motor 171 according to described rotary manipulation amount.
Fig. 3 c is that the rocking arm one fast control valve 150 that Fig. 3 a probably is shown is in non-switched neutral condition, and cantilever one fast control valve 110 is in the circuit diagram of transition status.
With reference to Fig. 3 c, the described first branch signal pipeline 103a is tangent disconnected with the oil extraction pipeline by described cantilever one fast control valve 110.And the working oil of the first pump P1 is confluxed in the working oil of the cantilever one fast parallel pipeline 111 and the first pump P1 by the first interflow pipeline 196 by the working oil that the first walking control valve 100 supplies to described cantilever one fast control valve 110, the three pump P3.Under this state, described cantilever one fast parallel pipeline 111 directly advances the parallel pipeline 172 with described rotation of valve 190 by the first interflow pipeline 196 and walking and is communicated with.And then, when to the 112 bigger loads of effect of described cantilever cylinder and the pressure of cantilever one fast parallel pipeline 111 during greater than the pressure of the parallel pipeline 172 of described rotation, the working oil of the described first pump P1 by described cantilever one fast parallel pipeline 111, the first interflow pipeline 196 and valve 190 is directly advanced in walking and can adverse current to the parallel pipeline 172 of described rotation.The adverse current of this working oil reduces the flow of the working oil that supplies to cantilever cylinder 112 and obviously reduces the actuating speed of cantilever cylinder 112.But, prevent adverse current by one-way valve 198 is set in the present embodiment, thereby the working oil of the described first pump P1 can supply to cantilever cylinder 112 by cantilever one fast control valve 110.In view of the above, not only can improve the actuating speed of cantilever cylinder 112, and can also further reduce rotational impact.
Fig. 4 probably shows the oil hydraulic circuit of other embodiment's the engineering machinery according to the present invention.
Other embodiment of the present invention is with the difference of foregoing one embodiment of the invention: the structure that valve 290 is directly advanced in walking is different.That is, other embodiment of the present invention changes between the 4th position 291 and the 5th position 292.
So, even if making walking directly advance valve 290 changes between two positions 291,292, therefore directly advance the signal pressure of the compression zone 290a of valve 290 and can change owing to be applied to described walking, can make walking directly advance valve 290 and carry out linear conversion according to the operation amount of walking operation unit 104.Thus, can prevent to walk directly to advance valve 290 to change, thereby can minimize rotational impact as the opening of the prior art/mode of closing.Because other structures are identical with foregoing one embodiment of the invention, the Therefore, omited describes in detail.
Claims (5)
1. the oil hydraulic circuit of an engineering machinery, it is characterized in that, have: first pump (P1) is used for supplying with working oil to first running motor (101) and the first forward position working machine (112,121) respectively by the first walking control valve (100) and the first forward position control valve (110,120) respectively; Second pump (P2) is used for supplying with working oil to second running motor (141) and the second forward position working machine (151) respectively by the second walking control valve (140) and the second forward position control valve (150) respectively; And the 3rd pump (P3), be used for supplying with working oil to revolution motor (171) by rotary control valve (170),
The oil hydraulic circuit of described engineering machinery comprises:
The first interflow pipeline (196), the working oil that is used for discharging from described the 3rd pump (P3) is also connected to the described first forward position control valve (110,120);
The second interflow pipeline (197) is used for the working oil of described the 3rd pump (P3) is also connected to the described second forward position control valve (150);
Oil extraction pipeline (195) is used for the working oil of described the 3rd pump (P3) is discharged by described rotary control valve (170);
Valve (190) is directly advanced in walking, according to the size of the signal pressure that is applied to compression zone (190a) (Pa4, Pb4, Pa5, Pb5), changes in the scope of first to the 3rd position (191,192,193); And
Rotate parallel pipeline (172), be used to make the circuitous described walking of working oil of described the 3rd pump (P3) directly to advance valve (190) and supply to described rotary control valve (170),
If described walking is directly advanced valve (190) and is transformed into described primary importance (191), then described the 3rd pump (P3) is communicated with the first aperture amount with described oil extraction pipeline (195), and described the 3rd pump (P3) was cut off with being connected of described first and second interflow pipeline (196,197)
If described walking is directly advanced valve (190) and is transformed into the described second place (192), then described the 3rd pump (P3) is communicated with the described first interflow pipeline (196) by first stream (192a), described the 3rd pump (P3) is communicated with the described second interflow pipeline (197) by second stream (192b), described the 3rd pump (P3) is communicated with described oil extraction pipeline (195) with the second aperture amount less than the first aperture amount by the 3rd stream (192c)
If described walking is directly advanced valve (190) and is transformed into described the 3rd position (193), then described the 3rd pump (P3) is communicated with described first and second interflow pipeline (196,197) respectively, and described the 3rd pump (P3) was cut off with being connected of described oil extraction pipeline (195).
2. the oil hydraulic circuit of engineering machinery according to claim 1 is characterized in that,
Also comprise shuttle valve unit (194), the big signal pressure of walk signal pressure (Pa4, Pb4, Pa5, Pb5) that is used for will put on described first and second walking control valve (100,140) is applied to described walking by the straight inlet signal pipeline (103) of walking and directly advances the compression zone of valve (190) (190a).
3. the oil hydraulic circuit of engineering machinery according to claim 2 is characterized in that,
Comprise: the first branch signal pipeline (103a), branch comes out from the straight inlet signal pipeline of described walking (103), and is connected to described oil extraction pipeline by described first and second walking control valve (100,140) successively; And
The second branch signal pipeline (103b) is connected to the oil extraction pipeline by described first and second forward position control valve (110,120,150) respectively,
In converting described first and second walking control valve (100,140) at least one breaks away from neutral condition, and when at least one in described first and second forward position control valve (110,120,150) broke away from neutral condition, described first and second branch signal pipeline (103a, 103b) was tangent disconnected with the oil extraction pipeline.
4. the oil hydraulic circuit of engineering machinery according to claim 1 is characterized in that,
Comprise that also being located at described the 3rd pump (P3) and described walking directly advances one-way valve (198) between the valve (190), collaborate pipeline (196) adverse current to the parallel pipeline of described rotation (172) by described first to be used to prevent working oil from described first pump (P1) is discharged.
5. the oil hydraulic circuit of an engineering machinery, it is characterized in that, have: first pump (P1) is used for supplying with working oil to first running motor (101) and the first forward position working machine (112,121) respectively by the first walking control valve (100) and the first forward position control valve (110,120) respectively; Second pump (P2) is used for supplying with working oil to second running motor (141) and the second forward position working machine (151) respectively by the second walking control valve (140) and the second forward position control valve (150) respectively; And the 3rd pump (P3), be used for supplying with working oil to revolution motor (171) by rotary control valve (170),
The oil hydraulic circuit of described engineering machinery comprises:
The first interflow pipeline (196), the working oil that is used for discharging from described the 3rd pump (P3) is also connected to the described first forward position control valve (110,120);
The second interflow pipeline (197) is used for the working oil of described the 3rd pump (P3) is also connected to the described second forward position working machine (151);
Oil extraction pipeline (195) is used for the working oil of described the 3rd pump (P3) is discharged by described rotary control valve (170);
Valve (290) is directly advanced in walking, according to the size of the signal pressure that is applied to compression zone (290a) (Pa4, Pb4, Pa5, Pb5), changes between the 4th position (291) and the 5th position (292);
Rotate parallel pipeline (172), circuitous described walking is directly advanced valve (290) and described the 3rd pump (P3) is connected with described rotary control valve (170); And
Shuttle valve unit (194), the big signal pressure of walk signal pressure (Pa4, Pb4, Pa5, Pb5) that is used for will put on described first and second walking control valve (100,140) is applied to described walking and directly advances the compression zone of valve (290) (290a),
If described walking is directly advanced valve (290) and is transformed into described the 4th position (291), then described the 3rd pump (P3) is communicated with described oil extraction pipeline (195), and described the 3rd pump (P3) was cut off with being connected of described first and second interflow pipeline (196,197),
If described walking is directly advanced valve (290) and is transformed into described the 5th position (292), then described the 3rd pump (P3) is communicated with described first and second interflow pipeline (196,197) respectively, and described the 3rd pump (P3) was cut off with being connected of described oil extraction pipeline (195).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR10-2008-0132181 | 2008-12-23 | ||
| KR1020080132181A KR101517240B1 (en) | 2008-12-23 | 2008-12-23 | Hydraulic circuit for construction machinery |
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| Publication Number | Publication Date |
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| CN101793272A true CN101793272A (en) | 2010-08-04 |
| CN101793272B CN101793272B (en) | 2013-07-10 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN2009102610665A Expired - Fee Related CN101793272B (en) | 2008-12-23 | 2009-12-22 | Hydraulic circuit for construction machinery |
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| KR (1) | KR101517240B1 (en) |
| CN (1) | CN101793272B (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104769286A (en) * | 2012-11-07 | 2015-07-08 | 萱场工业株式会社 | Fluid pressure control device for power shovel |
| CN110397100A (en) * | 2019-07-01 | 2019-11-01 | 上海三一重机股份有限公司 | Excavator control system, excavator and excavator control method |
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| KR101669680B1 (en) * | 2010-11-05 | 2016-10-26 | 두산인프라코어 주식회사 | Hydraulic circuit for construction machinery |
| JP6015157B2 (en) * | 2011-07-01 | 2016-10-26 | コベルコ建機株式会社 | Construction machinery |
| KR101971238B1 (en) * | 2013-09-16 | 2019-04-22 | 현대건설기계 주식회사 | Hydraulic system of construction equipment |
| KR102088062B1 (en) * | 2013-10-30 | 2020-04-14 | 두산인프라코어 주식회사 | Travel control apparatus of excavator |
| KR101693822B1 (en) | 2015-09-04 | 2017-01-09 | 훌루테크 주식회사 | hydraulic control system for construction machine |
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| CN110397100B (en) * | 2019-07-01 | 2021-10-29 | 上海三一重机股份有限公司 | Excavator control system, excavator and excavator control method |
Also Published As
| Publication number | Publication date |
|---|---|
| KR101517240B1 (en) | 2015-05-06 |
| KR20100073488A (en) | 2010-07-01 |
| CN101793272B (en) | 2013-07-10 |
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