CN106836363A - Loader hydraulic system - Google Patents
Loader hydraulic system Download PDFInfo
- Publication number
- CN106836363A CN106836363A CN201611251916.XA CN201611251916A CN106836363A CN 106836363 A CN106836363 A CN 106836363A CN 201611251916 A CN201611251916 A CN 201611251916A CN 106836363 A CN106836363 A CN 106836363A
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- China
- Prior art keywords
- valve
- steering
- pressure
- hydraulic system
- flow
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- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
-
- 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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- Engineering & Computer Science (AREA)
- Mining & Mineral Resources (AREA)
- Civil Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structural Engineering (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention discloses a kind of loader hydraulic system, belong to hydraulic system field.Including hydraulic oil container, the hydraulic oil container is connected with working barrel, steering pump, the working barrel is connected with banked direction control valves, shuttle valve, switch valve respectively by fluid pressure line, the banked direction control valves is connected with pilot valve, pressure selection valve, boom cylinder and rotary ink tank respectively, and wherein pressure selection valve is connected by shuttle valve with flow valve；The steering pump is connected with flow valve, switch valve respectively, and flow valve is connected by fluid pressure line with switch valve with pressure-gradient control valve, and pressure-gradient control valve is connected with steering gear, and steering gear is connected with steering cylinder, wherein being also associated with sequence valve between the flow valve and switch valve.The present invention is used for loading machine, realizes the purpose of the cost for reducing design, production and later maintenance, and reaches more preferable energy-saving effect.
Description
Technical field
The invention belongs to a kind of hydraulic system, specifically, more particularly to a kind of loader hydraulic system.
Background technology
In engineering machinery, loading machine typically carries out spading operation and loading operation, and whole machine frequently completes left and right turn, receives
Bucket, lifting, discharging etc. are acted, and these are required for hydraulic system to carry out control realization.It is general in existing loader hydraulic system
It is made up of machining device hydraulic system, steering hydraulic system.
Generally, the working barrel in machining device hydraulic system is supplied separately to the rotary ink tank in equipment and act
Oil-lifting jar, steering pump is supplied separately to steering cylinder, this to be independently supplied system to be easily caused the working barrel in turn up operating mode defeated
Go out most of flow and be in overflow situation, wasted power is larger；The pilot control of pilot control hydraulic system derives from pioneer pump,
The presence of pioneer pump increased the loss of power, and the maintenance cost in later stage can increase.
The content of the invention
It is an object of the invention to provide a kind of loader hydraulic system, to overcome hydraulic system power in the prior art to damage
Big, later maintenance cost problem high is lost, but also can avoid significantly transforming that the energy resource consumption for causing is increased with cost to ask
Topic.
To reach above-mentioned technique effect, the present invention is achieved by the following technical solutions：
A kind of loader hydraulic system, including hydraulic oil container, the hydraulic oil container are connected with working barrel, steering pump, described
Working barrel is connected with banked direction control valves, shuttle valve, switch valve respectively by fluid pressure line, and the banked direction control valves is selected with pilot valve, pressure respectively
The connection of valve, boom cylinder and rotary ink tank is selected, wherein pressure selection valve is connected by shuttle valve with flow valve；The steering pump difference
It is connected with flow valve, switch valve, flow valve is connected by fluid pressure line with switch valve with pressure-gradient control valve, pressure-gradient control valve connects with steering gear
Connect, steering gear is connected with steering cylinder, wherein being also associated with sequence valve between the flow valve and switch valve.
Further speaking, it is provided with filter between heretofore described hydraulic oil container and return line.
Further speaking, the heretofore described hydraulic pump of steering series connection of pumps the 3rd constitutes duplex pump configuration
Compared with prior art, the present invention has following beneficial effect：
(1) present invention has given up pioneer pump, and guide's energy source is from the output flow with working barrel and steering pump, and pressure is big
Be pilot control, it is achieved thereby that reduce design, production and later maintenance cost,
(2) present invention can realize that, in emergence working condition decline low power loss, increase is started by using sequence valve
The tractive force of machine.By way of the Small Flow Control flow conversion valve big flow with sequence valve, more preferable energy-saving effect is reached.
Brief description of the drawings
Fig. 1 is schematic diagram of the invention；
Fig. 2 is the A portions enlarged drawing of Fig. 1.
In figure：1st, working barrel；2nd, hydraulic oil container；3rd, pilot valve；4th, pressure selection valve；5th, shuttle valve；6th, flow valve；7th, turn to
Pump；8th, switch valve；9th, filter；10th, sequence valve；11st, pressure-gradient control valve；12nd, steering gear；13rd, steering cylinder；14th, banked direction control valves；15、
Boom cylinder；16th, rotary ink tank；17th, the 3rd hydraulic pump.
Specific embodiment
Below in conjunction with the accompanying drawings and specific embodiment is described further to the present invention.
As shown in Figure 1 and Figure 2, a kind of loader hydraulic system, including hydraulic oil container 2, the hydraulic oil container 2 and working barrel
1st, steering pump 7 is connected, and the working barrel 1 is connected with banked direction control valves 14, shuttle valve 5, switch valve 8 respectively by fluid pressure line, described many
Road valve 14 is connected with pilot valve 3, pressure selection valve 4, boom cylinder 15 and rotary ink tank 16 respectively, and wherein pressure selection valve 4 leads to
Shuttle valve 5 is crossed to be connected with flow valve 6；The steering pump 7 is connected with flow valve 6, switch valve 8 respectively, and flow valve 6 is equal with switch valve 8
It is connected with pressure-gradient control valve 11 by fluid pressure line, pressure-gradient control valve 11 is connected with steering gear 12, steering gear 12 is connected with steering cylinder 13.Its
Described in sequence valve 10 is also associated between flow valve 6 and switch valve 8.It was provided between the hydraulic oil container 2 and return line
Filter 9.Series connection the 3rd hydraulic pump 17 of the steering pump 7 constitutes duplex pump configuration.
With reference to above-described embodiment, action process and principle operationally of the invention is as follows：
When whole machine just starts, hydraulic system of working does not set up pressure, now steering wheel rotation, is driven by steering wheel
Steering gear 12, by steering for whole hydraulic system sets up pressure.By the pressure comparison of shuttle valve 5, the pressure that will be selected
Metering-in control system high.Working pressure range needed for making pressure be reduced to pilot system by pressure selection valve 4 again, so that
Supply pilot valve 3 works.The main valve plug of banked direction control valves 14 is promoted to cause that equipment is produced by the hydraulic oil liquid of pilot valve 3 corresponding
Action.Now, working barrel 1 generates pressure, and by the pressure comparison of shuttle valve 5, hydraulic oil liquid depressurizes by pressure selection valve 4
Supply pilot valve 3 is used as pilot control afterwards.
Restart after shutdown, the rodless cavity of boom cylinder 15 has back pressure, this pressure after pressure selection valve 4 by supplying first
Pilot valve 3 is moved so as to the main valve plug for promoting banked direction control valves 14 so that equipment produces corresponding action.Now, working barrel 1 is produced
Pressure, by the pressure comparison of shuttle valve 5, hydraulic oil liquid after the decompression of pressure selection valve 4 by supplying pilot valve 3 as guide oil
Source.Hydraulic system constantly circulates said process.
Constituted by increasing switch valve 8, flow valve 6, the 3rd hydraulic pump 17 of series connection of steering pump 7 in loader hydraulic system
Duplex pump, sequence valve 10, can by loading machine working barrel 1, the discharge capacity of steering pump 7 reduce, by flow valve 6 determine engine turn
Speed, then output pressure control signal pass to switch valve 8, control the 3rd hydraulic pump 17 of connecting of steering pump 7 to constitute by switch valve 8
Duplex pump realize engine in low speed to steering hydraulic system fuel feeding, so as to solve steering pump 7 during time of engine low speed
The not enough problem of fuel delivery.When high engine speeds are operated, said apparatus can be to hydraulic system of working fuel feeding, it is to avoid turn to liquid
There is larger power loss in pressure system.
In turn up operating mode, hydraulic system of working does not need big flow, and now, sequence valve 10 can automatically detect work
The pressure of system, when pressure be higher than turn up operating mode when, sequence valve 10 can cut off steering pump 7 in flow signal valve to flow conversion valve
Pressure feedback signal, thus cut-out interflow flow of the flow conversion control valve to hydraulic system of working, realize and use low discharge
The signal control of big flow is controlled, more preferable energy-saving effect is reached.Excess traffic enters cooling system simultaneously, by filter 9,
Return in hydraulic oil container 2, the temperature of hydraulic oil can be reduced, improve the stability and reliability of hydraulic system.
Claims (3)
1. a kind of loader hydraulic system, including hydraulic oil container (2), the hydraulic oil container (2) and working barrel (1), steering pump (7)
Connection, it is characterised in that：The working barrel (1) is connected with banked direction control valves (14), shuttle valve (5), switch valve (8) respectively by fluid pressure line
Connect, the banked direction control valves (14) connects with pilot valve (3), pressure selection valve (4), boom cylinder (15) and rotary ink tank (16) respectively
Connect, wherein pressure selection valve (4) is connected by shuttle valve (5) with flow valve (6)；The steering pump (7) respectively with flow valve (6),
Switch valve (8) is connected, and the flow valve (6) is connected by fluid pressure line with switch valve (8) with pressure-gradient control valve (11), described preferential
Valve (11) is connected with steering gear (12), and the steering gear (12) is connected with steering cylinder (13), the flow valve (6) and switch valve
(8) sequence valve (10) is also associated between.
2. loader hydraulic system according to claim 1, it is characterised in that：The hydraulic oil container (2) and return line
Between be provided with filter (9).
3. loader hydraulic system according to claim 1 and 2, it is characterised in that：The 3rd liquid of steering pump (7) series connection
Press pump (17) constitutes duplex pump configuration.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201611251916.XA CN106836363A (en) | 2016-12-30 | 2016-12-30 | Loader hydraulic system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201611251916.XA CN106836363A (en) | 2016-12-30 | 2016-12-30 | Loader hydraulic system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN106836363A true CN106836363A (en) | 2017-06-13 |
Family
ID=59113859
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201611251916.XA Withdrawn CN106836363A (en) | 2016-12-30 | 2016-12-30 | Loader hydraulic system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN106836363A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107268703A (en) * | 2017-07-06 | 2017-10-20 | 山东临工工程机械有限公司 | Loader hydraulic system |
| CN108179781A (en) * | 2018-01-31 | 2018-06-19 | 山东临工工程机械有限公司 | Loader hydraulic control system |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201581431U (en) * | 2009-12-18 | 2010-09-15 | 广西柳工机械股份有限公司 | Loader load sensitization hydraulic device |
| CN102518170A (en) * | 2011-12-27 | 2012-06-27 | 四川大学 | Hydraulic system of loading machine working device |
| CN104061196A (en) * | 2014-06-05 | 2014-09-24 | 安徽博一流体传动股份有限公司 | Novel hydraulic system for loader |
| CN204803957U (en) * | 2015-06-16 | 2015-11-25 | 山东临工工程机械有限公司 | Loader hydraulic system |
| CN105507362A (en) * | 2016-01-24 | 2016-04-20 | 吉林大学 | Hydraulic system of overflow-loss-free loader and control method of hydraulic system |
| JP2016125560A (en) * | 2014-12-26 | 2016-07-11 | 株式会社クボタ | Hydraulic system for work machine and work machine with the same |
-
2016
- 2016-12-30 CN CN201611251916.XA patent/CN106836363A/en not_active Withdrawn
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201581431U (en) * | 2009-12-18 | 2010-09-15 | 广西柳工机械股份有限公司 | Loader load sensitization hydraulic device |
| CN102518170A (en) * | 2011-12-27 | 2012-06-27 | 四川大学 | Hydraulic system of loading machine working device |
| CN104061196A (en) * | 2014-06-05 | 2014-09-24 | 安徽博一流体传动股份有限公司 | Novel hydraulic system for loader |
| JP2016125560A (en) * | 2014-12-26 | 2016-07-11 | 株式会社クボタ | Hydraulic system for work machine and work machine with the same |
| CN204803957U (en) * | 2015-06-16 | 2015-11-25 | 山东临工工程机械有限公司 | Loader hydraulic system |
| CN105507362A (en) * | 2016-01-24 | 2016-04-20 | 吉林大学 | Hydraulic system of overflow-loss-free loader and control method of hydraulic system |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107268703A (en) * | 2017-07-06 | 2017-10-20 | 山东临工工程机械有限公司 | Loader hydraulic system |
| CN108179781A (en) * | 2018-01-31 | 2018-06-19 | 山东临工工程机械有限公司 | Loader hydraulic control system |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| WW01 | Invention patent application withdrawn after publication | ||
| WW01 | Invention patent application withdrawn after publication |
Application publication date: 20170613 |