CN206221393U - Hydraulic system with flow-compensated function - Google Patents
Hydraulic system with flow-compensated function Download PDFInfo
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- CN206221393U CN206221393U CN201621094936.6U CN201621094936U CN206221393U CN 206221393 U CN206221393 U CN 206221393U CN 201621094936 U CN201621094936 U CN 201621094936U CN 206221393 U CN206221393 U CN 206221393U
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- valve
- mouthfuls
- hydraulic fluid
- unloading
- fluid ports
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Abstract
The utility model discloses a kind of hydraulic system with flow-compensated function, including pressure hydraulic oil container, variable pump, steering gear, flux amplification valve, steering cylinder, accumulator, determine variable control valve block, mode selection switch, unloading valve block, constant displacement pump, first segment discharge orifice, variable orifice, the first check valve, unloading valve, the second throttle orifice, the second check valve, unloading overflow valve, model selection magnetic valve.According to experimental results, the actual condition of incorporation engineering machinery optimizes the principle and structure of unloading valve block, and intergration model selection magnetic valve, can will determine variable system and directly switch quantitative system, improves adaptability for working condition；In addition, optimization steering hydraulic system fuel system, using the comfortableness and stability of flow-compensated further lifting steering.
Description
Technical field
The utility model is related to a kind of hydraulic system, more particularly, to a kind of hydraulic system with flow-compensated function.
Background technology
Hydraulic system is widely used in engineering machinery, and different purposes and the operating mode of complexity determine the complexity of hydraulic system
Property.Construction machinery hydraulic system common at present has Constant Pump System, constant displacement pump and variable pump combined system, entire variable pump system
System etc..Constant Pump System cost is relatively low, but energy loss is big；Entire variable energy saving of system effect is obvious, but relatively costly, no
Beneficial to popularity；Determine variable system will wherein some or certain several system variables, cost increases little, with respect to its energy-conservation
For effect, variable system is determined with cost performance higher.
Due in whole working, it is necessary to by whole machine hydraulic pressure in quantitative system, determine between variable system, entire variable system
Switching, so as to meet various construction operating modes, and general hydraulic system can not complete above-mentioned switching；Because variable system has one
Fixed response time, the swash plate of quick commutation variations per hour pump needs back row to become row again, causes moment underfed, and driver feels hand
Sense is heavy.
Utility model content
Technical problem to be solved in the utility model is the defect for overcoming prior art, there is provided one kind has flow-compensated
The hydraulic system of function, optimizes the principle and structure of unloading valve, and intergration model selection magnetic valve, can will determine variable system direct
Quantitative system is switched to, some special operation conditions are met；Using the accumulator of leading hydraulic system, for steering gear provides instantaneous stream
Amount, lifts steering stability and comfortableness.
In order to solve the above technical problems, the utility model provides a kind of hydraulic system with flow-compensated function, it is special
Levying is, including hydraulic oil container, variable pump, steering gear, flux amplification valve, steering cylinder, accumulator, determines variable control valve block, mould
Formula selecting switch, unloading valve block, constant displacement pump, hydraulic oil container inlet port respectively with variable pump, determine variable control valve block
T2 mouthfuls, the oil inlet of constant displacement pump, T mouthfuls of steering gear, the T5 hydraulic fluid ports of unloading valve block are connected；The oil-out and flow of the variable pump
P1 mouthfuls of amplifying valve is connected, while be connected with determine variable control valve block S1 mouthfuls, the X hydraulic fluid ports of the variable pump with determine Variable Control
The LS2 hydraulic fluid ports of valve block are connected；The steering gear respectively with flux amplification valve, determine variable control valve block and be connected；The Flow amplification
Valve respectively with steering cylinder, determine variable control valve block and be connected；The accumulator respectively with determine variable control valve block Xa hydraulic fluid ports, turn
It is connected to the oil inlet P mouthful of device；X1, X2, X3, XP hydraulic fluid port for determining variable control valve block is connected with leading hydraulic system, institute
State and determine A mouthfuls of variable control valve block and be connected with hydraulic system of working；The mode selection switch is selected with the pattern in unloading valve block
The magnet coil for selecting magnetic valve is connected；P5 mouthfuls of the unloading valve block is connected with the oil-out of constant displacement pump, the unloading valve block
Oil-out P6 is connected with the P2 hydraulic fluid ports for determining variable control valve block.
Further, the unloading valve block include model selection magnetic valve, unloading valve, variable orifice, first segment discharge orifice,
Second throttle orifice, the first check valve, the second check valve, unloading overflow valve, the model selection magnetic valve oil inlet and P6 mouthfuls of phase
Even；The oil return opening of the model selection magnetic valve is connected with T5 hydraulic fluid ports；The oil inlet of the unloading valve is connected with P5 hydraulic fluid ports；It is described
The oil-out of unloading valve is connected with T5 hydraulic fluid ports；After the variable orifice is in parallel with the first check valve, it is series at P5 hydraulic fluid ports and unloads
Between the control chamber of lotus valve；The P5 hydraulic fluid ports are controlled through the first of the spring cavity and unloading overflow valve of first segment discharge orifice and unloading valve
Chamber and oil inlet are connected；First control chamber of the unloading overflow valve is connected by model selection magnetic valve with P6 hydraulic fluid ports；It is described
The spring cavity of unloading overflow valve is connected after being connected with oil return opening with T5 hydraulic fluid ports；Second check valve is located at P5 hydraulic fluid ports and P6 hydraulic fluid ports
Between；Second throttle orifice is located between unloading valve spring cavity and the oil inlet of unloading overflow valve.
Further, R mouthfuls of the steering gear is connected with the R1 hydraulic fluid ports of flux amplification valve, L mouthfuls and stream of the steering gear
The L1 hydraulic fluid ports for measuring amplifying valve are connected.
Further, R2 mouthfuls of the flux amplification valve is connected with the rodless cavity of steering cylinder, the flux amplification valve
L2 mouthfuls is connected with the rod chamber of steering cylinder.
Further, EF mouthfuls of the flux amplification valve is connected with determine variable control valve block EF1 mouthfuls, the Flow amplification
T1 mouthfuls of valve is connected with determine variable control valve block T2 mouthfuls, LS mouthfuls of the flux amplification valve with the LS1 for determining variable control valve block
Mouth is connected.
Further, P mouthfuls respectively with steering gear of the S2 hydraulic fluid ports for determining variable control valve block, Xa hydraulic fluid ports is connected.
The beneficial effect that the utility model is reached：
（1）Engineering machinery can be determined variable system and directly switch to quantitative system, meet some special operation conditions, such as stacker
Condition demand；
（2）Using the accumulator of leading hydraulic system, for steering gear provides instantaneous delivery, lifting steering stability and comfortable
Property；
（3）Using integrated valve block, pipeline connection is reduced, simplify system；
（4）Constant displacement pump is protected using unloading valve block, prevents it from bearing impacting with high pressure, and overloaded in hydraulic system of working
Engine power is saved in journey；Magnetic valve can be selected by mode selection switch control model, and then control unloading valve block to realize
Unloading valve function or overflow valve function, so as to adapt to different duty requirements.
Brief description of the drawings
Fig. 1 is hydraulic system principle figure of the present utility model；
Fig. 2 is the structural representation of the utility model unloading valve block；
Fig. 3 is variable system steering pressure characteristic curve.
The implication of each Main Reference Numerals is in figure：
1. hydraulic oil container, 2. variable pump, 3. steering gear, 4. flux amplification valve, 5. steering cylinder, 6. accumulator, 7. fixed to become
Control valve block, 8. mode selection switch, 9. unloading valve block, 10. constant displacement pump, 11. first segment discharge orifices, 12. variable orifices,
13. first check valves, 14. unloading valves, 15. second throttle orifices, 16. second check valves, 17. unloading overflow valves, 18. model selections
Magnetic valve.
Specific embodiment
The utility model is further described below in conjunction with the accompanying drawings.Following examples are only used for clearly illustrating this
The technical scheme of utility model, and protection domain of the present utility model can not be limited with this.
As shown in figure 1, a kind of hydraulic system with flow-compensated function, including hydraulic oil container 1, variable pump 2, steering gear
3rd, flux amplification valve 4, steering cylinder 5, accumulator 6, determine variable control valve block 7, mode selection switch 8, unloading valve block 9, quantitative
Pump 10.
The inlet port respectively with variable pump 2 of the hydraulic oil container 1, determine variable control valve block 7 T2 mouthfuls, constant displacement pump 10 enter
Hydraulic fluid port, T mouthfuls of steering gear 3, the T5 hydraulic fluid ports of unloading valve block 9 are connected.The oil-out of the variable pump 2 and the P1 of flux amplification valve 4
Mouthful be connected, while be connected with determine variable control valve block 7 S1 mouthfuls, the X hydraulic fluid ports of the variable pump 2 with determine variable control valve block 7
LS2 hydraulic fluid ports are connected.
The steering gear 3 respectively with flux amplification valve 4, determine variable control valve block 7 and be connected, R mouthfuls of the steering gear 3 with stream
The R1 hydraulic fluid ports for measuring amplifying valve 4 are connected, and L mouthfuls of the steering gear 3 is connected with the L1 hydraulic fluid ports of flux amplification valve 4.It is described to determine variable control
P mouthfuls respectively with steering gear 3 of S2 hydraulic fluid ports, the Xa hydraulic fluid ports of valve block 7 processed is connected.
The flux amplification valve 4 respectively with steering cylinder 5, determine variable control valve block 7 and be connected, the flux amplification valve 4
R2 mouthfuls is connected with the rodless cavity of steering cylinder 5, and L2 mouthfuls of the flux amplification valve 4 is connected with the rod chamber of steering cylinder 5.It is described
EF mouthfuls of flux amplification valve 4 is connected with determine variable control valve block 7 EF1 mouthfuls, T1 mouthfuls of the flux amplification valve 4 with determine variable control
T2 mouthfuls of valve block 7 processed is connected, and LS mouthfuls of the flux amplification valve 4 is connected with determine variable control valve block 7 LS1 mouthfuls.
The accumulator 6 respectively with determine the Xa hydraulic fluid ports of variable control valve block 7, the oil inlet P mouthful of steering gear 3 is connected.It is described
X1, X2, X3, XP hydraulic fluid port for determining variable control valve block 7 are connected with leading hydraulic system, described the A for determining variable control valve block 7 mouthfuls with
Hydraulic system of working is connected.
The mode selection switch 8 is connected with the magnet coil of the model selection magnetic valve 18 in unloading valve block 9.It is described to unload
P5 mouthfuls of lotus valve block 9 is connected with the oil-out of constant displacement pump 10, the oil-out P6 of the unloading valve block 9 with determine variable control valve block 7
P2 hydraulic fluid ports be connected.
As shown in Fig. 2 the unloading valve block 9 includes model selection magnetic valve 18, unloading valve 14, variable orifice 12, the
One throttle orifice 11, the second throttle orifice 15, the first check valve 13, the second check valve 16, unloading overflow valve 17.
The oil inlet of model selection magnetic valve 18 is connected with P6 mouthfuls；The oil return opening and T5 of the model selection magnetic valve 18
Hydraulic fluid port is connected；The oil inlet of the unloading valve 14 is connected with P5 hydraulic fluid ports；The oil-out of the unloading valve 14 is connected with T5 hydraulic fluid ports；Institute
State variable orifice 12 it is in parallel with the first check valve 13 after, be series between the control chamber of P5 hydraulic fluid ports and unloading valve 14；The P5
Hydraulic fluid port is connected through first segment discharge orifice 11 with the spring cavity of unloading valve 14 and the first control chamber of unloading overflow valve 17 and oil inlet；Institute
The first control chamber for stating unloading overflow valve 17 is connected by model selection magnetic valve 18 with P6 hydraulic fluid ports；The unloading overflow valve 17
Spring cavity is connected after being connected with oil return opening with T5 hydraulic fluid ports；Second check valve 16 is located between P5 hydraulic fluid ports and P6 hydraulic fluid ports；It is described
Second throttle orifice 15 is located between the spring cavity of unloading valve 14 and the oil inlet of unloading overflow valve 17.
Specific implementation step is as follows：
1）Switching working mode：Under normal mode of operation, mode selection switch 8 must not electricity, the control of unloading overflow valve 17
Chamber is communicated by model selection magnetic valve 18 with P6 hydraulic fluid ports, and whether off-load is determined unloading valve block 9 by the pressure of P6 hydraulic fluid ports.Press mould
Formula selecting switch 8, model selection magnetic valve 18 obtains electric, and the control chamber of unloading overflow valve 17 is cut off, and now hydraulic system is by fixed
Variable system switches to quantitative system.Now, hydraulic system of working be quantitative system, steering hydraulic system be variable system, can
To reduce the tractive force of whole machine under combinational acting, stacking operating mode is adapted to.This kind of mode of operation applies also for light duty.
2）Steering hydraulic system is flow-compensated：From left to right in steering procedure, the rodless cavity internal high pressure of steering cylinder 5 passes through
Determine LS2 mouthfuls of variable control valve block 7 and feed back to X mouthfuls of variable pump 2；During commutation, the release of the rodless cavity internal pressure of steering cylinder 5,
The rod chamber internal pressure of steering cylinder 5 gradually rises, so X mouthfuls of pressure can again arrive height from high to low, as shown in figure 3, this time-varying
The amount discharge capacity of pump 2 also has one and arrives big process again from big to small, and in commutation moment, the pressure and flow of the output of variable pump 2 are equal
It is smaller, pressure and flow needed for being not sufficient to ensure that the normal work of steering gear 3, so occurring that commutation moment feel is heavy；When
During driver's quick rotation steering wheel, variable pump 2 needs the response time to increase discharge capacity, more fluids is exported, so can also go out
The situation that existing moment feel is aggravated.The utility model connects accumulator 6 with the oil inlet P mouthful of steering gear 3, due to accumulator 6
In be always maintained at the fluid of certain pressure and volume, can be compensated when the instantaneous delivery of variable pump 2 is not enough, reach the peak that disappears
Mend the effect of paddy.So, the feel and stability of steering are improved, and the comfortableness and stability of whole machine get a promotion.
3）Off-load is buffered and protection：By adjusting the pressure of unloading overflow valve 17, when the total load of hydraulic system of working exceedes
During setting value, unloading valve 14 is opened, only the fuel feeding of variable pump 2, so as to reduce equipment movement velocity, reduces internal system pressure
Power is impacted, and makes whole machine work more steady, safe.When mode selection switch 8 must not be electric, in the course of work, the P6 of unloading valve block 9
Hydraulic fluid port pressure rise, unloading valve block 9 starts off-load after reaching setting pressure, so as to protect constant displacement pump 10, prevents excess traffic from overflowing
Stream, saves engine power.Now, the high pressure of hydraulic system of working is born by variable pump 2, when system pressure is further raised
When, when reaching 2 cut-out pressure of variable pump, the discharge capacity of variable pump 2 is returned and is discharged to minimum automatically, eliminates spill losses.Implement process
It is as follows：When P6 hydraulic fluid port pressure reaches pressure unloading, unloading overflow valve 17 is opened, and P5 hydraulic fluid ports segment fluid flow is by first segment discharge orifice
11, then it flow to T5 mouthfuls by unloading overflow valve 17;The fluid for flowing through first segment discharge orifice 11 forms pressure differential at restriction two ends,
This pressure differential acts on the control chamber and spring cavity of unloading valve 14 so that unloading valve 14 is opened, and the second check valve 16 is high by P6 mouthfuls
Force feed is kept apart with P5 mouthfuls of low pressure oil, so as to protect constant displacement pump 10.In the opening process of unloading valve 14, the second throttle orifice 15 slows down
The valve element opening speed of unloading valve 14, prevents valve element from clashing into valve seat, extends the valve element life-span.When P6 hydraulic fluid ports pressure is less than setting pressure
When, unloading overflow valve 17 is closed, and flows through the flow vanishing of first segment discharge orifice 11, and the pressure at two ends difference of unloading valve 14 is reduced to zero, unloads
The valve element of lotus valve 14 resets under spring force, now due to the first check valve 13 and variable orifice 12 in the presence of, valve element
Reset speed it is controllable, so as to avoid compression shock caused by valve element quick closedown.
Certainly, above-described embodiment is only preferred scheme of the present utility model, is specifically not limited thereto, and on this basis may be used
Make according to actual needs with targetedly adjusting, so as to obtain different implementation methods.For example, in the base of above-described embodiment
Increase leading hydraulic system locking ball valve on plinth or magnetic valve, steering cylinder are changed into left and right two steering cylinders, steering gear and streams
Increase hydraulic stop valve, increase equipment control valve or oil cylinder between amount amplifying valve, increase oil return cleaner, increase hydraulic pressure
Oil radiator etc..Because mode in the cards is more, just no longer illustrate one by one here.
Claims (6)
1. there is the hydraulic system of flow-compensated function, it is characterized in that, including hydraulic oil container（1）, variable pump（2）, steering gear
（3）, flux amplification valve（4）, steering cylinder（5）, accumulator（6）, determine variable control valve block（7）, mode selection switch（8）, unload
Lotus valve block（9）, constant displacement pump（10）, the hydraulic oil container（1）Respectively with variable pump（2）Inlet port, determine variable control valve block（7）
T2 mouthfuls, constant displacement pump（10）Oil inlet, steering gear（3）T mouthfuls, unloading valve block（9）T5 hydraulic fluid ports be connected；The variable pump
（2）Oil-out and flux amplification valve（4）P1 mouthfuls be connected, while with determine variable control valve block（7）S1 mouthfuls be connected, the change
Amount pump（2）X hydraulic fluid ports with determine variable control valve block（7）LS2 hydraulic fluid ports be connected；The steering gear（3）Respectively with flux amplification valve
（4）, determine variable control valve block（7）It is connected；The flux amplification valve（4）Respectively with steering cylinder（5）, determine variable control valve block
（7）It is connected；The accumulator（6）Respectively with determine variable control valve block（7）Xa hydraulic fluid ports, steering gear（3）Oil inlet P mouthful phase
Even；It is described to determine variable control valve block（7）X1, X2, X3, XP hydraulic fluid port be connected with leading hydraulic system, it is described to determine variable control valve
Block（7）A mouthfuls be connected with hydraulic system of working；The mode selection switch（8）With unloading valve block（9）In model selection electromagnetism
Valve（18）Magnet coil be connected；The unloading valve block（9）P5 mouthfuls and constant displacement pump（10）Oil-out be connected, the unloading valve
Block（9）Oil-out P6 with determine variable control valve block（7）P2 hydraulic fluid ports be connected.
2. the hydraulic system with flow-compensated function according to claim 1, it is characterized in that, the unloading valve block（9）
Including model selection magnetic valve（18）, unloading valve（14）, variable orifice（12）, first segment discharge orifice（11）, the second throttle orifice
（15）, the first check valve（13）, the second check valve（16）, unloading overflow valve（17）, the model selection magnetic valve（18）Oil-feed
Mouth is connected with P6 mouthfuls；The model selection magnetic valve（18）Oil return opening be connected with T5 hydraulic fluid ports；The unloading valve（14）Oil-feed
Mouth is connected with P5 hydraulic fluid ports；The unloading valve（14）Oil-out be connected with T5 hydraulic fluid ports；The variable orifice（12）It is single with first
To valve（13）After parallel connection, P5 hydraulic fluid ports and unloading valve are series at（14）Control chamber between；The P5 hydraulic fluid ports are through first segment discharge orifice
（11）With unloading valve（14）Spring cavity and unloading overflow valve（17）The first control chamber and oil inlet be connected；The off-load overflow
Valve（17）The first control chamber pass through model selection magnetic valve（18）It is connected with P6 hydraulic fluid ports；The unloading overflow valve（17）Spring
Chamber is connected after being connected with oil return opening with T5 hydraulic fluid ports；Second check valve（16）Between P5 hydraulic fluid ports and P6 hydraulic fluid ports；Described
Two throttle orifices（15）Located at unloading valve（14）Spring cavity and unloading overflow valve（17）Oil inlet between.
3. the hydraulic system with flow-compensated function according to claim 1, it is characterized in that, the steering gear（3）R
Mouth and flux amplification valve（4）R1 hydraulic fluid ports be connected, the steering gear（3）L mouthfuls and flux amplification valve（4）L1 hydraulic fluid ports be connected.
4. the hydraulic system with flow-compensated function according to claim 1, it is characterized in that, the flux amplification valve
（4）R2 mouthfuls and steering cylinder（5）Rodless cavity be connected, the flux amplification valve（4）L2 mouthfuls and steering cylinder（5）Have bar
Chamber is connected.
5. the hydraulic system with flow-compensated function according to claim 1, it is characterized in that, the flux amplification valve
（4）EF mouthfuls with determine variable control valve block（7）EF1 mouthfuls be connected, the flux amplification valve（4）T1 mouthfuls with determine variable control valve
Block（7）T2 mouthfuls be connected, the flux amplification valve（4）LS mouthfuls with determine variable control valve block（7）LS1 mouthfuls be connected.
6. the hydraulic system with flow-compensated function according to claim 1, it is characterized in that, it is described to determine variable control valve
Block（7）S2 hydraulic fluid ports, Xa hydraulic fluid ports respectively with steering gear（3）P mouthfuls be connected.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201621094936.6U CN206221393U (en) | 2016-09-29 | 2016-09-29 | Hydraulic system with flow-compensated function |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201621094936.6U CN206221393U (en) | 2016-09-29 | 2016-09-29 | Hydraulic system with flow-compensated function |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN206221393U true CN206221393U (en) | 2017-06-06 |
Family
ID=58782774
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201621094936.6U Active CN206221393U (en) | 2016-09-29 | 2016-09-29 | Hydraulic system with flow-compensated function |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN206221393U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106224306A (en) * | 2016-09-29 | 2016-12-14 | 徐工集团工程机械股份有限公司科技分公司 | There is the hydraulic system of flow-compensated function |
-
2016
- 2016-09-29 CN CN201621094936.6U patent/CN206221393U/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106224306A (en) * | 2016-09-29 | 2016-12-14 | 徐工集团工程机械股份有限公司科技分公司 | There is the hydraulic system of flow-compensated function |
| CN106224306B (en) * | 2016-09-29 | 2019-03-15 | 徐工集团工程机械股份有限公司科技分公司 | Hydraulic system with flow-compensated function |
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| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| TR01 | Transfer of patent right | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20190605 Address after: 400051 Kowloon Park Incubation Building of Chongqing High-tech Development Zone Patentee after: XCMG CHONGQING ENGINEERING MACHINERY CO., LTD. Address before: 221000 No. 99 Kunpeng North Road, Xuzhou Economic Development Zone, Jiangsu Province Patentee before: Technology Branch of XCMG Engineering Machinery Co., Ltd. |