CN104728190A - Hydraulic energy-saving control system - Google Patents
Hydraulic energy-saving control system Download PDFInfo
- Publication number
- CN104728190A CN104728190A CN201410780181.4A CN201410780181A CN104728190A CN 104728190 A CN104728190 A CN 104728190A CN 201410780181 A CN201410780181 A CN 201410780181A CN 104728190 A CN104728190 A CN 104728190A
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- China
- Prior art keywords
- valve
- oil
- pump
- pressure oil
- hydraulic pump
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/14—Energy-recuperation means
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Operation Control Of Excavators (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
Provided is a hydraulic energy-saving control system. A change valve is arranged between an outlet of a guide pump and a volume adjustable hydraulic pump regulator; meanwhile a shuttle valve is arranged, the shuttle valve is used for choosing negative feedback pressure oil of a main control valve and pressure oil of the guide pump, and providing the pressure oil for the volume adjustable hydraulic pump regulator. An inlet of the shuttle valve is connected with a second change valve in a series mode in a control oil way. In the control oil way, one end of the second change valve is connected with an oil outlet of the guide pump. The other end of an inlet of the shuttle valve is connected with an oil inlet end of a throttle overflow valve. An outlet of the shuttle valve is connected with a first control oil way to communicate with a regulator. The two ends of the throttle overflow valve are connected with a first change valve in a parallel mode. The hydraulic energy-saving control system has the advantages that when an engineering vehicle is in a ready mode, minimum displacement control is carried out on the volume adjustable hydraulic pump through the pressure oil of the guide pump, and pressure oil of the volume adjustable hydraulic pump passes through the first change valve and directly returns to an oil tank, so that energy loss due to the fact that the pressure oil of the volume adjustable hydraulic pump passes through a negative feedback throttle valve in the ready state is solved.
Description
Technical field
The present invention relates to technical field of hydraulic, particularly a kind of hydraulic energy-saving control system being mainly used in hydraulic driving engineering vehicle.
Background technique
Use the engineering vehicle that inverted flux control hydraulic system drives, when standby, the pressure oil that volume adjustable hydraulic pump is discharged flows back to fuel tank through spool meta after reverse feedback throttle valve, being adjusted to minimum injection rate to make main pump realizes energy-conservation, pressure oil is introduced variable delivery hydraulic pump-regulating mechanism before throttle valve and controls
oil hydraulic pump.referring to circuit diagram shown in Fig. 1.
Summary of the invention
Object of the present invention is just to provide one when engineering vehicle is in holding state, the pressure oil of pioneer pump is utilized to carry out minimum injection rate control to volume adjustable hydraulic pump, and volume adjustable hydraulic pump pressure oil flows through a selector valve and directly gets back to fuel tank, thus improve the hydraulic energy-saving control system of the energy loss that standby variations per hour prexxure of the hydraulic pump oil produces because flowing through reverse feedback throttle valve.
Solution of the present invention is such:
Basic technical scheme of the present invention is: can continue when normally working to make engineering vehicle to use the characteristic of reverse feedback throttle valve to control variable displacercent pump, between guide's pump discharge to variable delivery hydraulic pump governor, being provided with a selector valve; Meanwhile, arrange after main control valve reverse feedback pressure oil and pioneer pump pressure oil are selected by a shuttle valve and be supplied to variable delivery hydraulic pump governor.
The concrete technological scheme of the present invention is: a kind of hydraulic energy-saving control system, comprise volume adjustable hydraulic pump, pioneer pump, the pressure oil of pioneer pump is utilized to carry out minimum injection rate control to variable displacement pump, it is characterized in that: the oil circuit control that the import being provided with shuttle valve is connected with the second selector valve, in this oil circuit control, one end of the second selector valve connects described pilot valve oil outlet, the other end connecting joint stream relief valve oil inlet end of shuttle valve import, described shuttle valve outlet connection first oil circuit control is to be communicated with regulator; Be connected to the first selector valve at described throttling relief valve two ends.
Technological scheme also comprises more specifically: connect described pilot valve oil outlet again after described second selector valve front end series connection second throttle.
Further: the connection position of described second selector valve increases throttle orifice
Further: described pilot valve oil outlet is connected with the 3rd throttle valve, be other mechanism's fuel feeding.
Advantage of the present invention is when engineering vehicle is in holding state, the pressure oil of pioneer pump is utilized to carry out minimum injection rate control to volume adjustable hydraulic pump, and volume adjustable hydraulic pump pressure oil flows through a selector valve and directly gets back to fuel tank, thus improve the energy loss that standby variations per hour prexxure of the hydraulic pump oil produces because flowing through reverse feedback throttle valve.
Accompanying drawing explanation
Fig. 1 is a structural representation of conventional hydraulic energy-saving control system.
Fig. 2 is the structural representation of the embodiment of the present invention 1.
Fig. 3 is the structural representation of the embodiment of the present invention 2.
Fig. 4 is the structural representation of the embodiment of the present invention 3.
Fig. 5 is the structural representation of the embodiment of the present invention 4.
Fig. 6 is the control loop embodiment schematic diagram that the present invention is applied to bucket cylinder on certain type excavator.
Fig. 7 is the schematic diagram that system shown in Figure 6 guiding valve 8 is operated in left position.
In accompanying drawing, each parts detail is: shuttle valve 1, throttling relief valve 2, first selector valve 3, second selector valve 4, controller 5, pressure switch 6, regulator 7, guiding valve 8, prime mover 9, volume adjustable hydraulic pump 10, the first pioneer pump 11, relief valve 12, first oil circuit control 13, second oil circuit control 14, feedback oil circuit 15, working connection 16, the 3rd oil circuit control 17, first guide's oil circuit 18, second guide's oil circuit 19, first throttle valve 20, second throttle 21, the 3rd throttle valve 22, pilot valve 23, solenoid valve 24, valve block 25, bucket cylinder 26.
Embodiment
The present invention uses the characteristic of reverse feedback throttle valve to control variable displacercent pump to continue when making engineering vehicle normally work, between guide's pump discharge to variable delivery hydraulic pump governor, be provided with a selector valve; Meanwhile, arranging after main control valve reverse feedback pressure oil and pioneer pump pressure oil are selected by a shuttle valve and be supplied to variable delivery hydraulic pump governor, is embodiments of the invention as follows.
Embodiment 1:
As shown in Figure 2, comprise volume adjustable hydraulic pump 10, pioneer pump 11, the pressure oil of pioneer pump is utilized to carry out minimum injection rate control to variable displacement pump, the oil circuit control that the import being provided with shuttle valve 1 is connected with the second selector valve 4, in this oil circuit control, one end of the second selector valve 4 connects described pioneer pump 11 oil outlet, the other end connecting joint stream relief valve 2 oil inlet end of shuttle valve 1 import, described shuttle valve 1 exports connection first oil circuit control 13 to be communicated with regulator 7; The first selector valve 3 is connected at described throttling relief valve 2 two ends.
Embodiment 2:
As shown in Figure 3, be on the basis of embodiment 1, connect described pilot valve 11 oil outlet again by after described second selector valve 4 front end series connection second throttle 21.
Embodiment 3:
As shown in Figure 4, be on the basis of embodiment 1, the connection position of described second selector valve 4 is increased throttle orifice.
Embodiment 4:
As shown in Figure 5, being on the basis of embodiment 1, being connected with the 3rd throttle valve 22 at described pilot valve 11 oil outlet, is other mechanism's fuel feeding.
Fig. 6 is for being applied to the control loop embodiment of bucket cylinder on certain type excavator by structure shown in the embodiment of the present invention 2, second oil circuit control 14 and feedback oil circuit 15 enter regulator 7 by the first oil circuit control 13 after shuttle valve 1, carry out discharge capacity adjustment to volume adjustable hydraulic pump 10.Throttling relief valve 2 is in parallel with the first selector valve 3, and the second selector valve 4 is connected in the second oil circuit control 14.The head pressure oil of volume adjustable hydraulic pump 10 flows back to fuel tank through guiding valve 8, working connection 16, throttling relief valve 2 or the first selector valve 3.The discharge of pioneer pump 11 flows back to fuel tank through first throttle valve 20, the 3rd oil circuit control 17, guiding valve 8.Relief valve 12 limits the maximum pressure of pioneer pump 11 head pressure oil.The switching of the first selector valve 3 and the second selector valve 4 is controlled by controller 5.Pressure switch 6 provides input signal to controller 5.Below for Fig. 6, introduce the working principle of this hydraulic energy-saving control system.
After prime mover 9 starts, volume adjustable hydraulic pump 10 and pioneer pump 11 are driven, and are sucked by hydraulic oil from fuel tank, then become high pressure oil and discharge, the pressure oil that volume adjustable hydraulic pump 10 is discharged flows through guiding valve 8, and the pressure oil that pioneer pump 11 is discharged is supplied to pilot valve 23 through valve block 25 and solenoid valve 24.When pilot valve 23 do not operate be in meta time, guiding valve 8 is also in meta, 3rd oil circuit control 17 pressure is zero, namely pressure switch 6 does not collect pressure signal, this Time Controller 5 sends instruction and exports control signal to the first selector valve 3 and the second selector valve 4 respectively, make two selector valve switch operating positions, now, the pressure oil that pioneer pump 11 is discharged flows through second throttle 21, second selector valve 4, shuttle valve 3, volume adjustable hydraulic pump regulator 7 is entered after first oil circuit control 13, the discharge capacity of volume adjustable hydraulic pump 10 is adjusted to minimum, and the effect of second throttle 21 pressure of pioneer pump 11 head pressure oil is reduced to the pilot pressure 3.2MPa being suitable for regulator 7, meanwhile, the pressure oil that volume adjustable hydraulic pump 10 is discharged flows back to fuel tank after guiding valve 8, working connection 16, first selector valve 3.The pressure oil of discharging due to volume adjustable hydraulic pump 10 does not flow through original throttling relief valve 2, so do not have energy loss.
Described in the preceding paragraph, when operating pilot valve 23, when namely requiring that bucket cylinder 26 moves, such as, operated pilot valve 23 makes spring 23-1 to pressing down, the P mouth of pressure oil from pilot valve 23 after valve block 25 and solenoid valve 24 that pioneer pump 11 is discharged flows to 1 mouthful through internal oil passages, guiding valve 8 promotes to the right by the left side control chamber then entering guiding valve 8 through guide's oil circuit 18, guiding valve 8 is made to be operated in left position, as shown in Figure 7, the pressure oil that now volume adjustable hydraulic pump 10 is discharged enters bucket cylinder 26 cavity of resorption through guiding valve 8, promotes cylinder piston rod and stretches out; And now, because guiding valve 8 is operated in left position, oil circuit control 17 is truncated and can not flows back to fuel tank, therefore pressure switch 6 establishes pressure, after this pressure signal enters controller 5, by the control logic of controller 5, stop exporting control signal to selector valve 3 and 4, make selector valve 3 and 4 be operated in initial position, namely this hydraulic system is restored to original negative feedback control loop, keeps engineering vehicle to utilize degenerative performance normally to work.
Pioneer pump 11 of the present invention can also be the pressure oil-source that other energy consumption is lower.
Claims (4)
1. a hydraulic energy-saving control system, comprise volume adjustable hydraulic pump (10), pioneer pump (11), the pressure oil of pioneer pump is utilized to carry out minimum injection rate control to variable displacement pump, it is characterized in that: the oil circuit control that the import being provided with shuttle valve (1) is connected with the second selector valve (4), in this oil circuit control, one end of the second selector valve (4) connects described pioneer pump (11) oil outlet, the other end connecting joint stream relief valve (2) oil inlet end of shuttle valve (1) import, described shuttle valve (1) outlet connection first oil circuit control (13) is to be communicated with regulator (7); Be connected to the first selector valve (3) at described throttling relief valve (2) two ends.
2. hydraulic energy-saving control system according to claim 1, is characterized in that: connect described pioneer pump (11) oil outlet again after described second selector valve (4) front end series connection second throttle (21).
3. hydraulic energy-saving control system according to claim 1, is characterized in that: the connection position of described second selector valve (4) increases throttle orifice.
4. hydraulic energy-saving control system according to claim 1, is characterized in that: described pioneer pump (11) oil outlet is connected with the 3rd throttle valve (22), is other mechanism's fuel feeding.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410780181.4A CN104728190A (en) | 2014-12-17 | 2014-12-17 | Hydraulic energy-saving control system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410780181.4A CN104728190A (en) | 2014-12-17 | 2014-12-17 | Hydraulic energy-saving control system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN104728190A true CN104728190A (en) | 2015-06-24 |
Family
ID=53452442
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410780181.4A Pending CN104728190A (en) | 2014-12-17 | 2014-12-17 | Hydraulic energy-saving control system |
Country Status (1)
| Country | Link |
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| CN (1) | CN104728190A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108005988A (en) * | 2018-01-29 | 2018-05-08 | 徐工集团工程机械有限公司 | Delay braking control valve, hydraulic system and excavator |
| CN108286538A (en) * | 2017-01-10 | 2018-07-17 | 斗山英维高株式会社 | The hydraulic system of engineering machinery |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4022023A (en) * | 1974-08-27 | 1977-05-10 | Kabushiki Kaisha Komatsu Seisakusho | Hydraulic circuit for controlling actuators in a construction vehicle |
| CN2610133Y (en) * | 2003-03-14 | 2004-04-07 | 柯坚 | Quantitative variable confluent system of loader |
| US20090025380A1 (en) * | 2007-07-24 | 2009-01-29 | Parker Hannifin Corporation, An Ohio Corporation | Fixed/variable hybrid system |
| CN101550830A (en) * | 2009-05-18 | 2009-10-07 | 浙江大学 | Energy-efficient shield cutterhead closed loop hydraulic control system adopting ganged accumulators |
| CN102912823A (en) * | 2012-11-09 | 2013-02-06 | 浙江大学 | Rotary energy saving system of excavator |
| CN103882906A (en) * | 2013-12-30 | 2014-06-25 | 华侨大学 | Excavator negative flow system sensitive to load |
-
2014
- 2014-12-17 CN CN201410780181.4A patent/CN104728190A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4022023A (en) * | 1974-08-27 | 1977-05-10 | Kabushiki Kaisha Komatsu Seisakusho | Hydraulic circuit for controlling actuators in a construction vehicle |
| CN2610133Y (en) * | 2003-03-14 | 2004-04-07 | 柯坚 | Quantitative variable confluent system of loader |
| US20090025380A1 (en) * | 2007-07-24 | 2009-01-29 | Parker Hannifin Corporation, An Ohio Corporation | Fixed/variable hybrid system |
| CN101550830A (en) * | 2009-05-18 | 2009-10-07 | 浙江大学 | Energy-efficient shield cutterhead closed loop hydraulic control system adopting ganged accumulators |
| CN102912823A (en) * | 2012-11-09 | 2013-02-06 | 浙江大学 | Rotary energy saving system of excavator |
| CN103882906A (en) * | 2013-12-30 | 2014-06-25 | 华侨大学 | Excavator negative flow system sensitive to load |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108286538A (en) * | 2017-01-10 | 2018-07-17 | 斗山英维高株式会社 | The hydraulic system of engineering machinery |
| CN108005988A (en) * | 2018-01-29 | 2018-05-08 | 徐工集团工程机械有限公司 | Delay braking control valve, hydraulic system and excavator |
| CN108005988B (en) * | 2018-01-29 | 2023-12-08 | 江苏徐工工程机械研究院有限公司 | Delay brake control valve, hydraulic system and excavator |
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| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20150624 |
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| RJ01 | Rejection of invention patent application after publication |