CN208816427U - Close flux controllable loader dual-pump combining hydraulic system - Google Patents
Close flux controllable loader dual-pump combining hydraulic system Download PDFInfo
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- CN208816427U CN208816427U CN201821365689.8U CN201821365689U CN208816427U CN 208816427 U CN208816427 U CN 208816427U CN 201821365689 U CN201821365689 U CN 201821365689U CN 208816427 U CN208816427 U CN 208816427U
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Abstract
The utility model discloses a kind of flux controllable loader dual-pump combining hydraulic system of conjunction, belong to hydraulic control system technical field, including hydraulic oil container, working hydraulic pressure control system and steering hydraulic control system, working hydraulic pressure control system includes: working barrel, pilot handle, multi-way valve and oil cylinder, wherein the inlet port of working barrel is connected with hydraulic oil container, multi-way valve respectively with the oil outlet of working barrel, oil cylinder and pilot handle are connected, steering hydraulic control system includes steering pump and pressure-gradient control valve, wherein the inlet port of steering pump connects hydraulic oil container, the oil outlet of steering pump connects pressure-gradient control valve, pressure-gradient control valve is also connected with flow control valve and diverter, one end of flow control valve connects the multi-way valve in working hydraulic pressure control system by shuttle valve group, the other end connects hydraulic oil container, different pressure signals can be exported according to shuttle valve group to control The opening of flow control valve, and then the uninterrupted at interflow is controlled, solve the problem in the prior art.
Description
Technical field
Flux controllable loader dual-pump combining hydraulic system is closed the utility model relates to a kind of, belongs to hydraulic control system
Technical field.
Background technique
Loader dual-pump combining hydraulic system refers to the control by steering hydraulic system pressure-gradient control valve, the flow of steering pump
After preferential satisfaction turns to, extra flow goes hydraulic system of working to collaborate.
If Fig. 1 is traditional loader dual-pump combining hydraulic system, specific work process is as follows:
The hydraulic oil that steering pump 8 comes out enters pressure-gradient control valve 7, and when no steering operation, the flow of steering pump all passes through excellent
First valve EF mouthfuls are gone hydraulic system of working to collaborate, and when diverter has go to action, steering load signal is anti-by pressure-gradient control valve LS mouthfuls
When presenting pressure-gradient control valve spring cavity, according to the size of load signal, to adjust the opening of 7 spool of pressure-gradient control valve, and then meet needed for steering
Flow, extra flow goes work system to collaborate by EF mouthful, therefore goes the uninterrupted at work system interflow cannot basis
The demand of work system goes to control, but the forces traffic of steering system goes work system to collaborate, therefore increases flow process
The local pressure loss of multi-way valve 3 and being lost along stroke pressure for pipeline, especially when work system is in high-pressure low-flow work
When condition, most of flow high pressure kicks oil return box, system energy loss is big, and system is not energy saving enough.
Utility model content
Flux controllable loader dual-pump combining hydraulic system, Neng Gougen are closed the purpose of this utility model is to provide a kind of
Different pressure signals is exported according to shuttle valve group to control the opening of flow control valve, and then controls the uninterrupted at interflow, is solved
The problem in the prior art.
It is described in the utility model to close flux controllable loader dual-pump combining hydraulic system, including hydraulic oil container, work
Hydraulic control system and steering hydraulic control system, working hydraulic pressure control system are connected with steering hydraulic control system, working solution
Pressure control system and steering hydraulic control system are connected with hydraulic oil container, and working hydraulic pressure control system includes: working barrel, guide
Handle, multi-way valve and oil cylinder, wherein the inlet port of working barrel is connected with hydraulic oil container, and multi-way valve is fuel-displaced with working barrel respectively
Mouthful, oil cylinder and pilot handle be connected, steering hydraulic control system includes steering pump and pressure-gradient control valve, wherein the inlet port of steering pump
Hydraulic oil container is connected, the oil outlet of steering pump connects pressure-gradient control valve, and pressure-gradient control valve is also connected with flow control valve and diverter, flow control
One end of valve processed connects the multi-way valve in working hydraulic pressure control system by shuttle valve group, and the other end connects hydraulic oil container.
The shortcomings that for transmission loading machine dual-pump combining hydraulic system, increase by 1 on traditional dual-pump combining hydraulic system
A shuttle valve group and 1 flow control valve, export different pressure signals according to shuttle valve group to control the opening of flow control valve, into
And the uninterrupted at control zone work system interflow.
The oil cylinder includes left and right elevating ram and rotary ink tank.
The B2 mouth of the multi-way valve is connected with the small chamber of left and right elevating ram, the A2 mouth and left and right elevating ram of multi-way valve
Big chamber be connected, B1 mouth of multi-way valve is connected with the small chamber of rotary ink tank, and the big chamber of the A1 mouth rotary ink tank of multi-way valve is connected, more
The T1 mouth of road valve is connected with hydraulic oil container.
The 2B mouth of the pilot handle is connected with the a2 of multi-way valve mouth, the b2 mouth phase of the 2A mouth and multi-way valve of pilot handle
Even, the 1A mouth of pilot handle is connected with the a1 of multi-way valve mouth, and the 1B mouth of pilot handle is connected with the b1 of multi-way valve mouth, pilot handle
P3 mouth be connected with pilot oil source, the T3 mouth of pilot handle is connected with hydraulic oil container.
The EF mouth of the pressure-gradient control valve is connected with the P4 of flow control valve mouth, CF mouth and the diverter import phase of pressure-gradient control valve
Even, the LS1 mouth of pressure-gradient control valve is connected with the LS of diverter mouth, and the T2 mouth of pressure-gradient control valve is connected with hydraulic oil container.
The X1 mouth of the shuttle valve group is connected with the b1 of multi-way valve mouth, and the X2 mouth of shuttle valve group is connected with the a2 of multi-way valve mouth,
The X3 mouth of shuttle valve group is connected with the a1 of multi-way valve mouth, and the X4 mouth of shuttle valve group is connected with the b2 of multi-way valve mouth.
The X mouth of the shuttle valve group is connected with the K1 of flow control valve mouth.
The P4 mouth of the flow control valve is connected with the EF of pressure-gradient control valve mouth, the P5 mouth of flow control valve and going out for working barrel
Mouth is connected, and the T4 mouth of flow control valve is connected with hydraulic oil container.
The inlet port of the working barrel is connected with hydraulic oil container, and oil outlet H and the P1 of the multi-way valve mouth of working barrel are connected,
The inlet port of steering pump is connected with hydraulic oil container, and oil outlet P6 and the P2 of the pressure-gradient control valve mouth of steering pump are connected.
The flow control valve uses proportional control valve.
The utility model compared with prior art, has the following beneficial effects:
It is described in the utility model to close flux controllable loader dual-pump combining hydraulic system, it can be exported according to shuttle valve group
Different pressure signals controls the opening of flow control valve, and then controls the uninterrupted at interflow；When hydraulic system of working work
Make in high-pressure low-flow, can control the interflow amount of hydraulic system of working, avoid unnecessary spill losses and along journey
Loss, improves the energy-saving effect of system；When individually turning to or without turning to, reduce the middle bit loss for entering multi-way valve after collaborating
The linear loss of mistake and entire pipeline.Solves the problem in the prior art.
Detailed description of the invention
Fig. 1 is traditional loader dual-pump combining hydraulic system schematic diagram；
Fig. 2 is loader dual-pump combining hydraulic system schematic diagram in the utility model embodiment；
In figure: 1, hydraulic oil container；2, working barrel；3, multi-way valve；4, rotary ink tank；5, left and right elevating ram；6, guide's hand
Handle；7, pressure-gradient control valve；8, steering pump；9, flow control valve；10, shuttle valve group.
Specific embodiment
The utility model is further described with reference to the accompanying drawings and examples:
Embodiment 1:
As Fig. 1 be traditional loader dual-pump combining hydraulic system, including hydraulic oil container 1, working hydraulic pressure control system and
Steering hydraulic control system, working hydraulic pressure control system are connected with steering hydraulic control system, working hydraulic pressure control system and turn
It is connected to hydraulic control system with hydraulic oil container 1, the inlet port of working barrel 2 is connected with hydraulic oil container 1,2 oil outlet H of working barrel
It is connected with the P1 of multi-way valve 3 mouth, the B2 mouth of multi-way valve 3 is connected with the small chamber of elevating ram 5, the A2 mouth and lifting oil of multi-way valve 3
The big chamber of cylinder 5 is connected, and B1 mouthful are connected with the small chamber of tipping bucket cylinder 4, and the big chamber of A1 mouthfuls of tipping bucket cylinders 4 is connected, T1 mouthfuls with 1 phase of hydraulic oil container
Even；The 2B of pilot handle 6 is connected with the a2 of multi-way valve 3 mouth, and 2A mouthfuls are connected with b2 mouthfuls, and 1A mouthfuls are connected with a1 mouthfuls, and 1B mouthfuls and b1 mouthfuls
It is connected, P3 mouthfuls are connected with pilot oil source, and T3 mouthfuls are connected with hydraulic oil container 1；The inlet port of steering pump 8 is connected with hydraulic oil container 1, out
Hydraulic fluid port P6 is connected with the P2 of pressure-gradient control valve 7 mouth, and the EF mouth of pressure-gradient control valve 7 is connected with the outlet H of working barrel 2, the CF of pressure-gradient control valve 7 and steering
Device import is connected, and the LS1 mouth of pressure-gradient control valve 7 is connected with LS mouthfuls of diverter, and the T2 mouth of pressure-gradient control valve 7 is connected with hydraulic oil container 1.
Specific work process is as follows: the hydraulic oil that steering pump 8 comes out enters pressure-gradient control valve 7, when no steering operation, steering pump
The EF mouth that 8 flow all passes through pressure-gradient control valve 7 goes hydraulic system of working to collaborate, when diverter has go to action, steering load
When signal passes through the spring cavity of the LS mouth feedback priority valve 7 of pressure-gradient control valve 7, according to the size of load signal, to adjust 7 valve of pressure-gradient control valve
The opening of core, and then meet the flow needed for turning to, extra flow goes work system to collaborate by the EF mouth of pressure-gradient control valve 7, because
This uninterrupted for going work system to collaborate cannot go to control according to the demand of work system, but steering hydraulic control system
Forces traffic goes work system to collaborate, thus increase flow by multi-way valve 3 local pressure loss and pipeline along journey
The pressure loss, especially when work system is in high-pressure low-flow operating condition, most of flow high pressure kicks return hydraulic oil container 1,
System energy loss is big, and system is not energy saving enough.
As shown in Fig. 2, described in the utility model close flux controllable loader dual-pump combining hydraulic system, including hydraulic
Fuel tank 1, working hydraulic pressure control system and steering hydraulic control system, working hydraulic pressure control system and steering hydraulic control system phase
Even, working hydraulic pressure control system and steering hydraulic control system are connected with hydraulic oil container 1, and working hydraulic pressure control system includes:
Working barrel 2, pilot handle 6, multi-way valve 3 and oil cylinder, wherein the inlet port of working barrel 2 is connected with hydraulic oil container 1, and multi-way valve 3 divides
It is not connected with the oil outlet of working barrel 2, oil cylinder and pilot handle 6, steering hydraulic control system includes steering pump 8 and pressure-gradient control valve
7, wherein the inlet port of steering pump 8 connects hydraulic oil container 1, and the oil outlet of steering pump 8 connects pressure-gradient control valve 7, and pressure-gradient control valve 7 is also connected with
Flow control valve 9 and diverter, one end of flow control valve 9 connect the multichannel in working hydraulic pressure control system by shuttle valve group 10
Valve 3, the other end connect hydraulic oil container 1.
In order to further illustrate above-described embodiment, oil cylinder includes left and right elevating ram 5 and rotary ink tank 4.
In order to further illustrate above-described embodiment, the B2 mouth of multi-way valve 3 is connected with the small chamber of left and right elevating ram 5, multichannel
The A2 mouth of valve 3 is connected with the big chamber of left and right elevating ram 5, and the B1 mouth of multi-way valve 3 is connected with the small chamber of rotary ink tank 4, multi-way valve 3
A1 mouth rotary ink tank 4 big chamber be connected, the T1 mouth of multi-way valve 3 is connected with hydraulic oil container 1.
In order to further illustrate above-described embodiment, the 2B mouth of pilot handle 6 is connected with the a2 of multi-way valve 3 mouth, pilot handle 6
2A mouth be connected with the b2 of multi-way valve 3 mouth, the 1A mouth of pilot handle 6 is connected with the a1 of multi-way valve 3 mouth, the 1B mouth of pilot handle 6
It is connected with the b1 of multi-way valve 3 mouth, the P3 mouth of pilot handle 6 is connected with pilot oil source, the T3 mouth and hydraulic oil container 1 of pilot handle 6
It is connected.
In order to further illustrate above-described embodiment, the EF mouth of pressure-gradient control valve 7 is connected with the P4 of flow control valve 9 mouth, pressure-gradient control valve 7
CF mouth be connected with diverter import, the LS1 mouth of pressure-gradient control valve 7 is connected with the LS of diverter mouth, the T2 mouth and hydraulic oil of pressure-gradient control valve 7
Case 1 is connected.
In order to further illustrate above-described embodiment, the X1 mouth of shuttle valve group 10 is connected with the b1 of multi-way valve 3 mouth, shuttle valve group 10
X2 mouthfuls are connected with the a2 of multi-way valve 3 mouth, and the X3 mouth of shuttle valve group 10 is connected with the a1 of multi-way valve 3 mouth, the X4 mouth of shuttle valve group 10 and more
The b2 mouth of road valve 3 is connected.
In order to further illustrate above-described embodiment, the X mouth of shuttle valve group 10 is connected with the K1 of flow control valve 9 mouth.
In order to further illustrate above-described embodiment, the P4 mouth of flow control valve 9 is connected with the EF of pressure-gradient control valve 7 mouth, flow control
The P5 mouth of valve 9 processed is connected with the outlet of working barrel 2, and the T4 mouth of flow control valve 9 is connected with hydraulic oil container 1.
In order to further illustrate above-described embodiment, the inlet port of working barrel 2 is connected with hydraulic oil container 1, working barrel 2 it is fuel-displaced
Mouthful H is connected with the P1 of multi-way valve 3 mouth, and the inlet port of steering pump 8 is connected with hydraulic oil container 1, the oil outlet P6 of steering pump 8 with preferentially
The P2 mouth of valve 7 is connected.
In order to further illustrate above-described embodiment, flow control valve 9 uses proportional control valve.
The working principle of the present embodiment are as follows: when independent turn to, 10 no pressure of shuttle valve group is exported at this time, flow control valve 9
Work is in bottom, therefore the oil circuit for going work system to collaborate is obstructed, and the flow of steering pump 8 goes to turn to by the CF mouth of pressure-gradient control valve 7
Device meets extra flow after steering system and directly returns hydraulic oil container 1 after the EF of pressure-gradient control valve 7 mouth enters flow control valve 9,
Enter the middle bit-loss of multi-way valve 3 and the linear loss of entire pipeline after reducing interflow.
Essentially identical with independent steering principle when without steering, 6 attonity of pilot handle, the flow of steering pump 8 all passes through
Flow control valve 9 returns hydraulic oil container 1, avoids the linear loss of the local losses and pipeline by multi-way valve 3.
When pilot handle 6 has movement, the pressure signal that pilot handle 6 exports is separately connected multi-way valve 3 and shuttle valve group 10,
The output pressure of shuttle valve group 10 connects the non-spring cavity of flow control valve 9, since flow control valve 9 is controlled using ratio, first
When leading the pivot angle difference of handle 6, the pressure that shuttle valve group 10 exports is also different, and then the opening of flow control valve 9 is also different, therefore
The flow collaborated into working hydraulic pressure control system is also different, i.e. 6 output pressure of pilot handle is bigger, and flow control valve 9 is open
Bigger, interflow amount is bigger.
By controlled thus according to the pivot angle difference of pilot handle 6 interflow amount, therefore when working hydraulic pressure control system into
When entering high-pressure low-flow operating condition, spill losses can be avoided, is reduced according to the different control interflow amount of 6 pivot angle of pilot handle
The energy loss of system, reduces fuel consumption.
Using the flux controllable loader dual-pump combining of the conjunction of the embodiments of the present invention being described in conjunction with the accompanying above
Hydraulic system can export different pressure signals according to shuttle valve group 10 to control the opening of flow control valve 9, and then control and close
The uninterrupted of stream solves the problem in the prior art.But the utility model is not limited to described embodiment,
Variation, modification, replacement and the change that these carry out embodiment in the case where not departing from the principles of the present invention and spirit
Shape is still fallen in the protection scope of the utility model.
Claims (10)
1. a kind of close flux controllable loader dual-pump combining hydraulic system, including hydraulic oil container (1), working hydraulic pressure control system
And steering hydraulic control system, working hydraulic pressure control system are connected with steering hydraulic control system, working hydraulic pressure control system and
Steering hydraulic control system is connected with hydraulic oil container (1), it is characterised in that: the working hydraulic pressure control system includes: work
(2), pilot handle (6), multi-way valve (3) and oil cylinder are pumped, wherein the inlet port of working barrel (2) is connected with hydraulic oil container (1), more
Road valve (3) is connected with the oil outlet of working barrel (2), oil cylinder and pilot handle (6) respectively, and steering hydraulic control system includes turning
To pump (8) and pressure-gradient control valve (7), wherein the inlet port of steering pump (8) connects hydraulic oil container (1), the oil outlet connection of steering pump (8)
Pressure-gradient control valve (7), pressure-gradient control valve (7) are also connected with flow control valve (9) and diverter, and one end of flow control valve (9) passes through shuttle valve
Group (10) connects the multi-way valve (3) in working hydraulic pressure control system, and the other end connects hydraulic oil container (1).
2. according to claim 1 close flux controllable loader dual-pump combining hydraulic system, it is characterised in that: described
Oil cylinder includes left and right elevating ram (5) and rotary ink tank (4).
3. according to claim 2 close flux controllable loader dual-pump combining hydraulic system, it is characterised in that: described
The B2 mouth of multi-way valve (3) is connected with the small chamber of left and right elevating ram (5), A2 mouth and the left and right elevating ram (5) of multi-way valve (3)
Big chamber is connected, and the B1 mouth of multi-way valve (3) is connected with the small chamber of rotary ink tank (4), the A1 mouth rotary ink tank (4) of multi-way valve (3)
Big chamber is connected, and the T1 mouth of multi-way valve (3) is connected with hydraulic oil container (1).
4. according to claim 1 close flux controllable loader dual-pump combining hydraulic system, it is characterised in that: described
The 2B mouth of pilot handle (6) is connected with the a2 mouth of multi-way valve (3), the b2 mouth phase of the 2A mouth and multi-way valve (3) of pilot handle (6)
Even, the 1A mouth of pilot handle (6) is connected with the a1 mouth of multi-way valve (3), the b1 mouth of the 1B mouth and multi-way valve (3) of pilot handle (6)
It is connected, the P3 mouth of pilot handle (6) is connected with pilot oil source, and the T3 mouth of pilot handle (6) is connected with hydraulic oil container (1).
5. according to claim 1 close flux controllable loader dual-pump combining hydraulic system, it is characterised in that: described
The EF mouth of pressure-gradient control valve (7) is connected with the P4 mouth of flow control valve (9), and the CF mouth of pressure-gradient control valve (7) is connected with diverter import, preferentially
The LS1 mouth of valve (7) is connected with the LS of diverter mouth, and the T2 mouth of pressure-gradient control valve (7) is connected with hydraulic oil container (1).
6. according to claim 1 close flux controllable loader dual-pump combining hydraulic system, it is characterised in that: described
The X1 mouth of shuttle valve group (10) is connected with the b1 mouth of multi-way valve (3), and the X2 mouth of shuttle valve group (10) is connected with the a2 mouth of multi-way valve (3),
The X3 mouth of shuttle valve group (10) is connected with the a1 mouth of multi-way valve (3), and the X4 mouth of shuttle valve group (10) is connected with the b2 mouth of multi-way valve (3).
7. according to claim 1 close flux controllable loader dual-pump combining hydraulic system, it is characterised in that: described
The X mouth of shuttle valve group (10) is connected with the K1 mouth of flow control valve (9).
8. according to claim 1 close flux controllable loader dual-pump combining hydraulic system, it is characterised in that: described
The P4 mouth of flow control valve (9) is connected with the EF mouth of pressure-gradient control valve (7), the outlet of the P5 mouth and working barrel (2) of flow control valve (9)
It is connected, the T4 mouth of flow control valve (9) is connected with hydraulic oil container (1).
9. according to claim 1 close flux controllable loader dual-pump combining hydraulic system, it is characterised in that: described
The inlet port of working barrel (2) is connected with hydraulic oil container (1), and the oil outlet H of working barrel (2) is connected with the P1 mouth of multi-way valve (3), turns
It is connected to the inlet port of pump (8) with hydraulic oil container (1), the oil outlet P6 of steering pump (8) is connected with the P2 mouth of pressure-gradient control valve (7).
10. according to claim 1 close flux controllable loader dual-pump combining hydraulic system, it is characterised in that: described
Flow control valve (9) use proportional control valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201821365689.8U CN208816427U (en) | 2018-08-23 | 2018-08-23 | Close flux controllable loader dual-pump combining hydraulic system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201821365689.8U CN208816427U (en) | 2018-08-23 | 2018-08-23 | Close flux controllable loader dual-pump combining hydraulic system |
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| Publication Number | Publication Date |
|---|---|
| CN208816427U true CN208816427U (en) | 2019-05-03 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201821365689.8U Active CN208816427U (en) | 2018-08-23 | 2018-08-23 | Close flux controllable loader dual-pump combining hydraulic system |
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| CN (1) | CN208816427U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111851618A (en) * | 2020-07-30 | 2020-10-30 | 雷沃工程机械集团有限公司 | Method and system for solving problem of slow bucket collecting speed of constant-variable flow converging system |
| CN112682373A (en) * | 2020-12-29 | 2021-04-20 | 山推工程机械股份有限公司 | Hydraulic system, control method and engineering vehicle |
-
2018
- 2018-08-23 CN CN201821365689.8U patent/CN208816427U/en active Active
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111851618A (en) * | 2020-07-30 | 2020-10-30 | 雷沃工程机械集团有限公司 | Method and system for solving problem of slow bucket collecting speed of constant-variable flow converging system |
| CN112682373A (en) * | 2020-12-29 | 2021-04-20 | 山推工程机械股份有限公司 | Hydraulic system, control method and engineering vehicle |
| CN112682373B (en) * | 2020-12-29 | 2023-03-21 | 山推工程机械股份有限公司 | Hydraulic system, control method and engineering vehicle |
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