CN104405708B - Load-sensitive analog valve and loader load-reacting system - Google Patents
Load-sensitive analog valve and loader load-reacting system Download PDFInfo
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- CN104405708B CN104405708B CN201410477784.7A CN201410477784A CN104405708B CN 104405708 B CN104405708 B CN 104405708B CN 201410477784 A CN201410477784 A CN 201410477784A CN 104405708 B CN104405708 B CN 104405708B
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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
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- Physics & Mathematics (AREA)
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- Fluid-Pressure Circuits (AREA)
Abstract
The present invention relates to load-sensitive analog valve and loader load-reacting system, for solving the shortcoming that existing load-sensitive valve arrangement is complicated, cost is high, disclosure one load-sensitive analog valve, it controls valve hydraulic control end and entrance and connects, controls the outlet of valve with hydraulic control K mouth and servo valve entrance turns on, the outlet of servo valve is connected with the entrance of flow control valve, the non-spring cavity of valve rod of servo valve connects with oil-feed P mouth, and the spring cavity of servo valve connects with oil-feed P1 mouth；The oil-out of the oil-in connecting joint discharge orifice of flow control valve, the oil-out of flow control valve connects oil return T mouth, the non-spring terminal of valve rod of flow control valve connects outlet and the oil-feed P mouth of described servo valve, and the valve rod spring terminal of flow control valve connects hydraulic control K slogan and LS mouth.This load-sensitive analog valve can fictitious load sensitive signal, there is simple in construction, the advantage that cost is low.
Description
Technical field
The present invention relates to a kind of hydraulic valve, the load-sensitive analog valve particularly relating to a kind of analog load signals feedback function and the loader load-reacting system with this load-sensitive analog valve.
Background technology
Maximum load-reacting system of application in loader hydraulic system.The main hydraulic of load-reacting system includes load-reacting pump, load-sensitive distributing valve, load-sensitive flux amplification valve, load-sensitive brake valve etc..Wherein load-sensitive distributing valve, load-sensitive flux amplification valve, load-sensitive brake valve has the element provided to load-reacting pump flow control valve feedback pressure signal according to load, so that load-reacting pump provides the flow of correspondence according to load pressure, it is achieved energy-conservation purpose.But at present owing to the valves such as load-sensitive distributing valve, load-sensitive flux amplification valve, load-sensitive brake valve are owing to being integrated with load feedback pressure signal function, therefore causing that these valve arrangements are extremely complex, manufacturing cost is high.
Summary of the invention
Present invention aims to the existing control valve arrangement with load-sensitive feedback signal complicated, shortcoming that cost is high and the load-sensitive analog valve that can provide load feedback pressure signal according to load pressure is provided and there is the loader load-reacting system of this load-sensitive analog valve.
The technical scheme is that and be achieved in that: a kind of load-sensitive analog valve of structure, it includes oil-feed P mouth, load LS mouth, oil-feed P1 mouth, hydraulic control K mouth, oil return T mouth, throttle orifice, flow control valve, servo valve, control valve, the hydraulic control end controlling valve all connects with hydraulic control K mouth with entrance, and the entrance of the entrance of control valve outlet with servo valve through controlling valve turns on when hydraulic control K mouth has pressure, when hydraulic control K mouth no pressure, the entrance of described servo valve turns on oil return T mouth with the 3rd mouthful through the outlet controlling valve；The non-spring cavity of valve rod of servo valve connects with oil-feed P mouth, and the valve rod spring cavity of servo valve connects with oil-feed P1 mouth；The oil-out of the oil-in connecting joint discharge orifice of flow control valve, the oil-out of flow control valve connects oil return T mouth, first hydraulic control mouth of the non-spring terminal of valve rod of flow control valve and the second hydraulic control mouth are connected respectively outlet and the oil-feed P mouth of servo valve, first hydraulic control mouth of the valve rod spring terminal of flow control valve and the second hydraulic control mouth are connected respectively hydraulic control K slogan and load LS mouth, load LS mouth is connected to the oil-out of throttle orifice, and the oil-in of throttle orifice is connected with oil-feed P mouth.
Loader load-reacting system solution provided by the invention is as follows: this system includes hydraulic actuation device, controls the main valve of hydraulic actuation device, the pilot valve of control bound, through main valve to the variable pump of hydraulic actuation device fuel feeding, fuel tank, also include above-mentioned load-sensitive analog valve and pilot operated valve device, the oil-feed P mouth of load-sensitive analog valve is connected with variable pump oil-out, load LS mouth is connected with the LS valve end of variable pump through pilot operated valve device, and oil-feed P1 mouth is connected with the main valve inlet of system；The hydraulic control end of hydraulic control K mouth and pilot operated valve device is all connected with pilot valve through shuttle valve, and oil return T mouth is connected with fuel tank；When pilot valve has pressure signal to export, the LS valve end of load LS mouth and variable pump turns on.
In above-mentioned loader load-reacting system, pilot operated valve device is two-position three-way valve, and its hydraulic control end and pilot-actuated valve are all connected with pilot valve through shuttle valve, makes load LS mouth turn on through the LS valve end of pilot operated valve device with variable pump when guide's end has pressure signal.
In above-mentioned loader load-reacting system, hydraulic actuation device is rotary ink tank and the boom cylinder of loader.
The present invention is compared with prior art, advantages of the present invention: load-sensitive analog valve is combined use with common hydraulic control main valve can provide the load feedback signal feeding back to variable pump according to load, variable pump is made to provide corresponding flow, realize variable delivery hydraulic system, but this analog valve has simple in construction with the combination of Normal hydraulic control bound compared with the Ioad-sensing control main valve with load-sensitive feedback signal, the advantage of low cost of manufacture, this analog valve is applied in loader hydraulic system, the function of Ioad-sensing control main valve can be obtained, but cost can be substantially reduced.
Accompanying drawing explanation
Fig. 1 is the structure principle chart of the load-sensitive analog valve of the present invention；
Fig. 2 be the present invention loader load-reacting system in the schematic diagram of hydraulic system of working.
Parts title and sequence number in figure:
Hydraulic oil container 1, variable pump 2, return oil filter 3, air relief valve 4, load-sensitive analog valve 5, pilot valve 6, rotary ink tank 7, boom cylinder 8, distributing valve 9, shuttle valve 11, pilot operated valve device 12, control valve 51, servo valve 52, flow control valve 53, throttle orifice 54.
Detailed description of the invention
Below in conjunction with accompanying drawing, specific embodiments is described.
The structure of load-sensitive analog valve is as shown in Figure 1: it includes oil-feed P mouth, load LS mouth, oil-feed P1 mouth, hydraulic control K mouth, oil return T mouth, throttle orifice 54, flow control valve 53, servo valve 52, controls valve 51, the hydraulic control end controlling valve 51 connects with hydraulic control K mouth with entrance A, and the entrance A controlling valve 51 when hydraulic control K mouth has pressure turns on the entrance D of servo valve 52 through the outlet B of control valve, when hydraulic control K mouth no pressure, the entrance D of servo valve 52 is through controlling three mouthfuls of C of outlet B and the and the conducting of oil return T mouth of valve 51；The non-spring cavity of valve rod of servo valve 52 connects with oil-feed P mouth, and the valve rod spring cavity of servo valve 52 connects with oil-feed P1 mouth；The oil-out of the oil-in connecting joint discharge orifice 54 of flow control valve 53, the oil-out of flow control valve 53 connects oil return T mouth, valve rod one end of flow control valve 53 is provided with spring, for valve rod spring terminal, other end does not set spring, for the non-spring terminal of valve rod, it is provided with two not connected liquid controling cavities at the non-spring terminal of valve rod, the outlet E of valve rod non-spring terminal the first hydraulic control mouth F of connection corresponding to the two liquid controling cavity and the second hydraulic control mouth G corresponding connection servo valve 52 respectively and oil-feed P mouth, the valve rod spring terminal of flow control valve 53 also is provided with two not connected liquid controling cavities, valve rod spring terminal the first hydraulic control mouth H and the second hydraulic control mouth J of connection corresponding to the two liquid controling cavity be corresponding connection hydraulic control K mouth and load LS mouth respectively, load LS mouth is connected to the oil-out of throttle orifice, the oil-in of throttle orifice is connected with oil-feed P mouth.
The operation principle of this analog valve is as follows: is controlled valve 51 by hydraulic control K mouth pressure signal and acts on left position, control entrance A and the outlet B conducting of valve 51, hydraulic control K mouth pressure signal is delivered to the non-spring terminal of valve rod of flow control valve 53 by the entrance D of servo valve 52 and outlet E, the valve rod of flow control valve 53 moves to right, the flow flowing through throttle orifice 54 reduces, the pressure reduction at throttle orifice 54 two ends reduces, the pressure of the feedback of load LS mouth just increases, when load LS mouth is connected with the LS valve end of variable pump, the pressure differential of the LS valve end of the pump intake pressure of variable pump and variable pump reduces, △ P when variable pump is for stable original state, it is necessary for increasing discharge capacity with the flow needed for adaptive system；Otherwise when the pressure of hydraulic control K mouth pressure signal reduces, flow through throttle orifice 54 flow to increase, throttle orifice 54 two ends pressure reduction increases, the pressure of the feedback of load LS mouth is reduced by, when load LS mouth is connected with the LS valve end of variable pump, pumping hole and the pressure differential fed back between variable pump LS valve of variable pump increase, and △ P when variable pump is for stable original state is necessary for reducing discharge capacity with the flow needed for adaptive system.When hydraulic control K mouth pressure signal stabilization, variable pump is according to providing suitable flow needed for system, if cause variable pump pump intake pressure because of load pressure change and enter the change of main valve inlet pressure, servo valve 52 moves left and right according to the pump intake pressure of variable pump is corresponding with main valve inlet pressure extent, and then increase or weaken the control pressure of servo valve 52 left end, make the real-time Displacement Regulation size of variable pump.
Loader load-reacting system provided by the invention (hydraulic steering system therein is not shown) as shown in Figure 2: this system includes hydraulic actuation device, control main valve namely the distributing valve 9 of hydraulic actuation device, control the pilot valve 6 of distributing valve 9, the allocated valve 9 is to the variable pump 2 of hydraulic actuation device fuel feeding, hydraulic oil container 1, also include aforesaid load-sensitive analog valve 5 and pilot operated valve device 12, the oil-feed P mouth of load-sensitive analog valve 5 is connected with variable pump 2 oil-out, load LS mouth is connected with the LS valve end of variable pump 2 through pilot operated valve device 12, oil-feed P1 mouth is connected with the working oil entrance of the distributing valve 9 of system；The hydraulic control end of hydraulic control K mouth and pilot operated valve device 12 is all connected with pilot valve 6 through shuttle valve 11, and oil return T mouth is connected with hydraulic oil container；When pilot valve 6 has pressure signal to export, the LS valve end of load LS mouth and variable pump turns on.Hydraulic actuation device is boom cylinder 8 and rotary ink tank 7.Pilot operated valve device 12 is two-position three-way valve, its hydraulic control end is connected with pilot valve 6 through shuttle valve 11, and when pilot valve 6 has pressure signal to export, pilot pressure is transferred to the hydraulic control end of pilot operated valve device 12 through shuttle valve 11, the spool making pilot operated valve device 12 moves, and causes load LS mouth to turn on through the LS valve end of pilot operated valve device 12 with variable pump.The oil-out of variable pump is connected with pilot valve 6 through air relief valve 4, is formed to the branch road of pilot valve 6 fuel feeding, and the oil return opening of the valve such as distributing valve 9, pilot valve 6 connects with hydraulic oil container 1 through return oil filter 3.
In this hydraulic system, no matter the pantograph linkage of pilot valve 6 is made or when rotating bucket is associated with action, namely the pressure signal of pilot valve 6 is delivered to hydraulic control K mouth and pilot operated valve device 12 right-hand member of load-sensitive analog valve 5 by shuttle valve 11, pilot pressure oil promotes pilot operated valve device 12 to act on right position, the load LS mouth of load-sensitive analog valve is turned on the LS valve end of variable pump, simultaneously, the pilot pressure signal of shuttle valve 11 transmission promotes the valve rod controlling valve 51 in load-sensitive analog valve 5 to move to right and act on left position, control entrance A and the outlet B conducting of valve 51, pilot pressure acts on the non-spring terminal of valve rod of flow control valve 53 by the entrance D of servo valve 52 and outlet E, make its valve rod move to right and cause that flow control valve 53 entrance to the flow of outlet reduces, namely the flow flowing through throttle orifice 54 reduces, throttle orifice 54 two ends pressure reduction reduces, the pumping hole of variable pump and the pressure differential feeding back to pump LS valve reduce, △ P when variable pump is for stable original state, it is necessary for increasing discharge capacity with the flow needed for adaptive system；Otherwise, when pilot pressure signal is by high voltage variable low pressure, variable pump delivery reduces accordingly, it is achieved the output flow of variable pump is followed the change of pilot pressure and changed therewith, wastes without flow, it is achieved energy-conservation；And when load pressure increase make variable pump outlet pressure equal to variable pump oil-out cut-out pressure own time, variable pump delivery is almost nil, is in high pressure waiting state, it is to avoid the high pressure kicks loss of system.
During pilot valve 6 attonity, distributing valve 9 is in and closes middle position state, equipment system does not need hydraulic oil, pilot operated valve device 12 acts on left position, and it is zero that the LS pressure oil of variable pump 2 connects pressure with fuel tank T, now, the Δ P that variable pump 2 oil-out pressure is set up in advance equal to LS valve, discharge capacity, close to zero, provides only the fluid met needed for system leak, it is to avoid middle bit-loss.And making the flow of throttle orifice 54 in load-sensitive analog valve 5 because of the cut-off of flow control valve 53 is zero, the pressure of load LS mouth is equal to the pressure of variable pumping hole.
When pilot valve 6 pressure is definite value, distributing valve 9 opening is certain, variable pump 2 provides required hydraulic oil also according to distributing valve aperture, now, when the change of outer load pressure causes that variable pump 2 outlet pressure changes, the pilot pressure changing the non-spring cavity of valve rod controlling flow control valve, the discharge capacity of adaptive adjustment variable pump 2 is moved left and right by the valve rod of servo valve 52 in load-sensitive analog valve 5.
Claims (4)
1. a load-sensitive analog valve, it is characterized in that including oil-feed P mouth, load LS mouth, oil-feed P1 mouth, hydraulic control K mouth, oil return T mouth, throttle orifice, flow control valve, servo valve, control valve, the hydraulic control end of described control valve all connects with hydraulic control K mouth with entrance and the entrance of described control valve turn on through the entrance controlling outlet and the servo valve of valve when hydraulic control K mouth has pressure, and when hydraulic control K mouth no pressure, the entrance of described servo valve turns on through the outlet of described control valve and the 3rd mouthful and oil return T mouth；The non-spring cavity of valve rod of described servo valve connects with oil-feed P mouth, and the spring cavity of described servo valve connects with oil-feed P1 mouth；The oil-out of the oil-in connecting joint discharge orifice of described flow control valve, the oil-out of described flow control valve connects oil return T mouth, first hydraulic control mouth of the non-spring terminal of valve rod of described flow control valve and the second hydraulic control mouth correspondence respectively connects outlet and the oil-feed P mouth of described servo valve, first hydraulic control mouth of the valve rod spring terminal of described flow control valve and the second hydraulic control mouth be correspondence connection hydraulic control K mouth and load LS mouth respectively, load LS mouth is connected to the oil-out of throttle orifice, and the oil-in of throttle orifice is connected with oil-feed P mouth.
2. a loader load-reacting system, including hydraulic actuation device, control the main valve of hydraulic actuation device, control bound pilot valve, through main valve to the variable pump of hydraulic actuation device fuel feeding, fuel tank, characterized by further comprising the load-sensitive analog valve in claim 1 and pilot operated valve device, the oil-feed P mouth of described load-sensitive analog valve is connected with variable pump oil-out, load LS mouth is connected with the LS valve end of variable pump through pilot operated valve device, and oil-feed P1 mouth is connected with the main valve inlet of system；The hydraulic control end of hydraulic control K mouth and pilot operated valve device is all connected with pilot valve through shuttle valve, and oil return T mouth is connected with fuel tank；When pilot valve has pressure signal to export, the LS valve end of described load LS mouth and variable pump turns on.
3. loader load-reacting system according to claim 2, it is characterised in that described pilot operated valve device is two-position three-way valve.
4. loader load-reacting system according to claim 2, it is characterised in that described hydraulic actuation device is rotary ink tank and the boom cylinder of loader.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410477784.7A CN104405708B (en) | 2014-09-18 | 2014-09-18 | Load-sensitive analog valve and loader load-reacting system |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410477784.7A CN104405708B (en) | 2014-09-18 | 2014-09-18 | Load-sensitive analog valve and loader load-reacting system |
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| Publication Number | Publication Date |
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| CN104405708A CN104405708A (en) | 2015-03-11 |
| CN104405708B true CN104405708B (en) | 2016-06-29 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201410477784.7A Active CN104405708B (en) | 2014-09-18 | 2014-09-18 | Load-sensitive analog valve and loader load-reacting system |
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Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107882798B (en) * | 2017-11-10 | 2019-08-20 | 广西柳工机械股份有限公司 | Load simulation valve and loading machine variable system |
| CN109578352A (en) * | 2019-01-28 | 2019-04-05 | 徐工消防安全装备有限公司 | Load sensitive system and aerial work platform |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH10267004A (en) * | 1997-03-25 | 1998-10-06 | Shin Caterpillar Mitsubishi Ltd | Fluid control method and device thereof |
| CN202673874U (en) * | 2012-06-25 | 2013-01-16 | 江苏海鹏特种车辆有限公司 | Constant-pressure variable control system of load sensitive hydraulic pump |
| CN202789861U (en) * | 2012-09-03 | 2013-03-13 | 山河智能装备股份有限公司 | Simple load sensory system |
| CN103671336B (en) * | 2013-12-12 | 2016-03-30 | 中联重科股份有限公司 | Load-sensitive hydraulic system and power matching control method, device and system |
| CN104029721B (en) * | 2014-01-23 | 2016-09-07 | 广西柳工机械股份有限公司 | Loader hydraulic transfer |
| CN203835840U (en) * | 2014-04-16 | 2014-09-17 | 徐工集团工程机械股份有限公司 | Plate type load-sensitive multi-tandem valve tail link |
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Effective date of registration: 20230406 Address after: 545007 the Guangxi Zhuang Autonomous Region Liuzhou City Liu Tai Road No. 1 Patentee after: GUANGXI LIUGONG MACHINERY Co.,Ltd. Patentee after: Guangxi Zhongyuan Machinery Co.,Ltd. Address before: 545007 the Guangxi Zhuang Autonomous Region Liuzhou City Liu Tai Road No. 1 Patentee before: GUANGXI LIUGONG MACHINERY Co.,Ltd. Patentee before: LIUZHOU LIUGONG HYDRAULIC COMPONENTS Co.,Ltd. |