CN106640817A - Pressure compensation type energy-saving control valve suitable for double-pump confluence and diversion hydraulic system - Google Patents
Pressure compensation type energy-saving control valve suitable for double-pump confluence and diversion hydraulic system Download PDFInfo
- Publication number
- CN106640817A CN106640817A CN201710005627.XA CN201710005627A CN106640817A CN 106640817 A CN106640817 A CN 106640817A CN 201710005627 A CN201710005627 A CN 201710005627A CN 106640817 A CN106640817 A CN 106640817A
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- China
- Prior art keywords
- pressure
- valve
- hydraulic fluid
- fluid ports
- hydraulic
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Classifications
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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
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/021—Valves for interconnecting the fluid chambers of an actuator
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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
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/026—Pressure compensating valves
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20546—Type of pump variable capacity
Abstract
The invention relates to engineering machines, in particular to a pressure compensation type energy-saving control valve suitable for a double-pump confluence and diversion hydraulic system. The pressure compensation type energy-saving control valve comprises a three-way pressure compensator, a damping hole, a one-way valve, a hydraulic control throttling valve, a pressure control valve, an unloading valve and oil ports. Control oil port connection is determined by a working load signal and a pilot control signal; the differential pressure of the hydraulic control throttling valve is set by the three-way pressure compensator; the opening degree of the hydraulic control throttling valve is regulated according to a pilot signal, and then the flow needed by a working system is output. A combination of the three-way pressure compensator and the hydraulic control throttling valve is additionally arranged in an existing double-pump confluence and diversion unloading system, so that an existing constant-displacement pump open-center overflow speed regulating system is upgraded into a constant-displacement pump load-sensitive system, low-pressure unloading of the working system is achieved through the bypass three-way pressure compensator, loading pressure self-adaptation of a constant-displacement pump is also achieved, and thus accurate flow output unrelated to load changes is achieved.
Description
Technical field
The present invention relates to engineering machinery, more particularly to a kind of energy-conservation control that shunting Load Relief System is closed suitable for loading machine double pump
Valve processed.
Background technology
Loading machine is that a kind of operating efficiency is high, broad-spectrum engineering machinery, and its hydraulic system is mainly by working hydraulic pressure system
System and steering hydraulic system composition.The existing loader hydraulic system overwhelming majority adopts double pump system, typically there is a steering pump
And working-machine pump, it is substantially effectively, using the flow of two pumps, now generally to adopt interflow pattern, i.e. double pump pressure-gradient control valve steering system
System and double pump close shunting Load Relief System.Double pump pressure-gradient control valve steering low cost, but loading machine is in combinational acting（Cut on loading machine side
Enter side lifting）Tractive force will not improve；Double pump closes shunting Load Relief System to be had double pump fuel feeding, turns to preferential, conjunction shunting, sets up
Pressure unloading function, rationally using engine power, improves overall operation efficiency, has become existing loader dual-pump combining
System preferred configuration.Another domestic existing loader hydraulic system has full fixed dilivery hydraulic system, determines variable delivery hydraulic system etc., job family
Using the system of constant displacement pump, therewith the widely used center six of opening of paced work system leads to banked direction control valves to system, and speed governing is using bypass
Throttling and the combination of meter in, its speed governing effect is throttled by valve rod, and control goes the amount of opening of oil cylinder and oil return box to come real
Existing.Overcome load pressure due to being the pressure set up by meter out, therefore governor control characteristics is by load pressure and oil pump stream
The impact of amount.Whole working load pressure be it is unstable vary, the flow of hydraulic pump makes it also being continually changing
Speed governing maneuvering performance is very unstable, manipulates difficult；And valve rod steering force is big, because load pressure change causes valve port △ P to become
Change, hydraulic power change causes valve rod steering force to change, and the scrambling of steering force makes vernier control more difficult.In a word, the oil
Road poor controllability, it is highly difficult that operator wants precise control control equipment, operator's sensation, experience is leaned on entirely and is sent out when participating in the cintest
Wave.
The content of the invention
For the problems referred to above, it is an object of the invention to propose closing suitable for double pump for a kind of energy-conservation and accurate output flow
The pressure compensation type energy-saving control valve of shunting hydraulic system.
It is that, up to above-mentioned purpose, the technical solution used in the present invention is：A kind of double pump that is applied to of construction closes shunting hydraulic system
Pressure compensation type energy-saving control valve, it is characterised in that：Include three-way pressure compensating device, damping hole, check valve, hydraulic-control throttling
Valve, pressure-control valve, unloader and P1 hydraulic fluid ports, P2 hydraulic fluid ports, P3 hydraulic fluid ports, LS1 hydraulic fluid ports, LS2 hydraulic fluid ports, T1 hydraulic fluid ports；Three-way pressure
The import of compensator is connected with the import of P1 mouths, unloader, check valve, the outlet of three-way pressure compensating device and off-load valve outlet port,
Pressure control valve outlet is connected after connecting with T1 mouths；One-way valved outlet is connected in the import of P3 hydraulic fluid ports, hydraulic-control throttling valve, and pressure
The Stress control mouth of force control valve；The spring cavity of unloader connects the import in pressure-control valve；P1 hydraulic fluid ports connect constant displacement pump, P2
Hydraulic fluid port connects work system, and P3 hydraulic fluid ports are connected with steering, and LS1 hydraulic fluid ports connection steering simultaneously transmits workload signal,
LS2 hydraulic fluid ports take from pilot control signal；Pressure reduction between P2 hydraulic fluid ports, the P3 hydraulic fluid ports of hydraulic-control throttling valve is set by three-way pressure compensating device
It is fixed；The aperture of the hydraulic-control throttling valve is adjusted according to pilot signal, output services system necessary flow.
The present invention sets up three-way pressure compensating device in existing double pump closes shunting Load Relief System and hydraulic-control throttling valve group is closed, and makes
Obtain current quantitative pump and open middle position overflowing and speed system upgrade into constant displacement pump load sensitive system, realize work system by bypass
Three-way pressure compensating device Low-pressure load discharge and constant displacement pump load pressure self adaptation, and then realize that the flow unrelated with load change is accurate
Output：
（1）In constant displacement pump pressure compensating system, when banked direction control valves does not work in middle position, pump is realized by three-way pressure compensating device
Off-load, to pumping up step-down and protective effect.Simultaneously three-way pressure compensating device pressure unloading is low, section when realizing that system does not work
Energy.
（2）When the system is operating, banked direction control valves import is poor with outlet pressure when three-way pressure compensating device ensure that load change
It is constant, system is realized and precisely exported with the load unrelated flow of change, that is, flow through the size and valve element of banked direction control valves flow
Displacement is relevant, unrelated with load variations；The load that the constant i.e. pressure compensator of pressure reduction before and after flow controller can not only very well be realized is mended
The effect of repaying, and it is poor that the outlet of pump can be made only to be higher by a level pressure than load pressure in real time, so as to realize that load pressure is adaptive
Should.
Description of the drawings
Fig. 1 is embodiment of the present invention schematic diagram.
Description of symbols in figure：1-three-way pressure compensating device, 2-damping hole, 3-check valve, 4-hydraulic-control throttling valve, 5-
Pressure-control valve, 6-unloader.
Specific embodiment
To further understand the present invention, technical scheme is done into one with reference to the accompanying drawings and detailed description
Step explanation, referring to Fig. 1：
The present embodiment is as shown in figure 1, the pressure compensation type energy-conservation that shunting hydraulic system is closed suitable for double pump according to embodiments of the present invention
Control valve is made up of three-way pressure compensating device 1, damping hole 2, check valve 3, hydraulic-control throttling valve 4, pressure-control valve 5, unloader 6,
And with P1 hydraulic fluid ports, P2 hydraulic fluid ports, P3 hydraulic fluid ports, LS1 hydraulic fluid ports, LS2 hydraulic fluid ports, T1 hydraulic fluid ports.The import of three-way pressure compensating device 1 and P1
Mouth, the import of unloader 6, check valve 3 are connected, and outlet and the unloader 6 of three-way pressure compensating device 1 are exported, pressure-control valve 5 goes out
Mouth is connected after connecting with T1 mouths；The outlet of check valve 3 is connected in the import of P3 hydraulic fluid ports, hydraulic-control throttling valve 4, and pressure-control valve 5
Stress control mouth；The spring cavity of unloader 6 is connected in the import of pressure-control valve 5.P1 hydraulic fluid ports connect the oil-out of constant displacement pump,
The banked direction control valves of P2 hydraulic fluid ports connection work system provides fluid, and P3 hydraulic fluid ports are connected with steering, LS1 hydraulic fluid ports transmission workload letter
Number give steering, decide whether to work system collaborate.LS2 hydraulic fluid ports take from pilot control signal, control the hydraulic-control throttling
The aperture of valve 4, so as to output services system necessary flow.Pressure reduction between P2 hydraulic fluid ports, the P3 hydraulic fluid ports of hydraulic-control throttling valve 4 is by threeway
Pressure compensator 1 sets.
The present invention operation principle be：
（1）When work system does not work.The pilot signal pressure of work system is zero, and hydraulic-control throttling valve 4 is in right position, at valve port
In closed mode, now three-way pressure compensating device 1 is in maximum open, the low pressure of fluid Jing three-way pressure compensatings device 1 of constant displacement pump
Off-load oil return box.Because the pilot signal pressure of work system is zero, valve core of multiway valve is in middle position, and workload signal pressure is
Zero, therefore LS1 hydraulic fluid port feedback-less oil pressure is transferred to steering, and then steering is not collaborated to work system.
（2）When work system works.When work system has pilot signal pressure to be input into, hydraulic-control throttling valve 4 is in opening
Pressure reduction is set up at state, the two ends of three-way pressure compensating device 1.When pressure reduction exceedes spring setting value, valve element is moved downward, and makes threeway pressure
Force compensating device 1 is connected with back oil road, and constant displacement pump is input into banked direction control valves by work system necessary flow, and excess traffic Jing three-way pressures are mended
Repay the direct oil return box of device 1；As pilot signal pressure is stepped up, the valve port opening of hydraulic-control throttling valve 4 is incrementally increased, hydraulic control section
Pressure reduction progressively reduces before and after stream valve 4, and then the three-way pressure compensating device 1 in flow control valve is progressively closed with drainback passage
Little, after pressure reduction is less than spring setting value, three-way pressure compensating device 1 is closed with drainback passage, and quantitative pump discharge fully enters work
Make system.Hydraulic-control throttling 4 imports of valve constant, the system poor with outlet pressure when three-way pressure compensating device 1 ensure that load change
Realize the flow unrelated with load change precisely to export, that is, the size for flowing into banked direction control valves flow is only relevant with spool displacement, with
Load change is unrelated；The load compensation effect of the constant i.e. pressure compensator of pressure reduction before and after hydraulic-control throttling valve 4 can not only be very well realized,
And it is poor that the outlet pressure of pump can be made only to be higher by a level pressure than load pressure in real time, so as to realize load pressure self adaptation.
（3）Work system pressure exceedes unloader.When work system pressure rise sets pressure to more than pressure-control valve 5
When, pressure-control valve 5 is opened, and constant displacement pump fluid is by unloader 6 with Low-pressure load discharge oil return box, and work system is independent by steering pump
Fuel feeding.
Claims (1)
- It is 1. a kind of that the pressure compensation type energy-saving control valve for shunting hydraulic system is closed suitable for double pump, it is characterised in that：Include three Logical pressure compensator（1）, damping hole（2）, check valve（3）, hydraulic-control throttling valve（4）, pressure-control valve（5）, unloader（6）, with And P1 hydraulic fluid ports, P2 hydraulic fluid ports, P3 hydraulic fluid ports, LS1 hydraulic fluid ports, LS2 hydraulic fluid ports, T1 hydraulic fluid ports；Three-way pressure compensating device（1）Import and P1 mouths, Unloader（6）, check valve（3）Import be connected, three-way pressure compensating device（1）Outlet and unloader（6）Outlet, Stress control Valve（5）Outlet is connected after connecting with T1 mouths；Check valve（3）Outlet is connected in P3 hydraulic fluid ports, hydraulic-control throttling valve（4）Import, and Pressure-control valve（5）Stress control mouth；Unloader（6）Spring cavity connect in pressure-control valve（5）Import；P1 hydraulic fluid ports connect Constant displacement pump is connect, P2 hydraulic fluid ports connection work system, P3 hydraulic fluid ports are connected with steering, and LS1 hydraulic fluid ports connection steering simultaneously transmits work Make load signal, LS2 hydraulic fluid ports take from pilot control signal；Hydraulic-control throttling valve（4）P2 hydraulic fluid ports, P3 hydraulic fluid ports between pressure reduction by three Logical pressure compensator（1）Setting；The hydraulic-control throttling valve（4）Aperture according to pilot signal adjust, needed for output services system Flow.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710005627.XA CN106640817B (en) | 2017-01-04 | 2017-01-04 | The pressure compensation type energy-saving control valve of shunting hydraulic system is closed suitable for double pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710005627.XA CN106640817B (en) | 2017-01-04 | 2017-01-04 | The pressure compensation type energy-saving control valve of shunting hydraulic system is closed suitable for double pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106640817A true CN106640817A (en) | 2017-05-10 |
| CN106640817B CN106640817B (en) | 2018-11-13 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710005627.XA Active CN106640817B (en) | 2017-01-04 | 2017-01-04 | The pressure compensation type energy-saving control valve of shunting hydraulic system is closed suitable for double pump |
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| CN (1) | CN106640817B (en) |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2727469Y (en) * | 2004-08-24 | 2005-09-21 | 上海彭浦巨力工程机械有限公司 | Load feedback pressure adaptation multiway valve |
| EP1616997A1 (en) * | 2004-07-13 | 2006-01-18 | Bosch Rexroth AG | Hydraulic control device |
| CN104895139A (en) * | 2015-06-12 | 2015-09-09 | 圣邦集团有限公司 | Constant-delivery pump and variable pump combined control system of loader |
| CN104929183A (en) * | 2015-05-21 | 2015-09-23 | 徐工集团工程机械股份有限公司科技分公司 | Loader constant and variable hydraulic system based on flow amplifying steering |
| CN205241000U (en) * | 2015-12-16 | 2016-05-18 | 广州大学 | Safe energy -conserving single cylinder hydraulic pressure elevator system |
| CN105986595A (en) * | 2015-02-04 | 2016-10-05 | 卡特彼勒（青州）有限公司 | Machine and hydraulic system for machine |
| 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 |
-
2017
- 2017-01-04 CN CN201710005627.XA patent/CN106640817B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1616997A1 (en) * | 2004-07-13 | 2006-01-18 | Bosch Rexroth AG | Hydraulic control device |
| CN2727469Y (en) * | 2004-08-24 | 2005-09-21 | 上海彭浦巨力工程机械有限公司 | Load feedback pressure adaptation multiway valve |
| CN105986595A (en) * | 2015-02-04 | 2016-10-05 | 卡特彼勒（青州）有限公司 | Machine and hydraulic system for machine |
| CN104929183A (en) * | 2015-05-21 | 2015-09-23 | 徐工集团工程机械股份有限公司科技分公司 | Loader constant and variable hydraulic system based on flow amplifying steering |
| CN104895139A (en) * | 2015-06-12 | 2015-09-09 | 圣邦集团有限公司 | Constant-delivery pump and variable pump combined control system of loader |
| CN205241000U (en) * | 2015-12-16 | 2016-05-18 | 广州大学 | Safe energy -conserving single cylinder hydraulic pressure elevator system |
| 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 |
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| Publication number | Publication date |
|---|---|
| CN106640817B (en) | 2018-11-13 |
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| PB01 | Publication | ||
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| CB02 | Change of applicant information | ||
| CB02 | Change of applicant information |
Address after: 317000 358, zhe Road, Dayang street, Taizhou, Zhejiang. Applicant after: Zhejiang Gaoyu Hydraulic Mechanical and Electrical Co., Ltd. Address before: 317000 No. 358, extension Road, Dayang street, Taizhou, Zhejiang. Applicant before: Zhejiang Gaoyu Hydraulic Mechanical and Electrical Co., Ltd. |
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