CN1136397C - Priority-type flow rate enlarging and merging valve - Google Patents
Priority-type flow rate enlarging and merging valve Download PDFInfo
- Publication number
- CN1136397C CN1136397C CNB001362429A CN00136242A CN1136397C CN 1136397 C CN1136397 C CN 1136397C CN B001362429 A CNB001362429 A CN B001362429A CN 00136242 A CN00136242 A CN 00136242A CN 1136397 C CN1136397 C CN 1136397C
- Authority
- CN
- China
- Prior art keywords
- valve
- spool
- priority
- oil
- pressure
- 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.)
- Expired - Fee Related
Links
Images
Landscapes
- Fluid-Pressure Circuits (AREA)
- Power Steering Mechanism (AREA)
Abstract
The present invention relates to a priority type flow rate magnifying and merging valve which comprises a valve body, a magnifying valve, a priority valve, a cone valve and a shuttle valve. When the guide oil on both ends of a magnifying valve core is cut off, the connection of left and right turning oil cylinder openings and a pressure oil inlet is cut off by a priority valve core; when the guide oil is pushed from the right of the magnifying valve core to the left of the magnifying valve core, the pressure oil inlet and the right turning oil cylinder opening are gradually communicated by the magnifying valve and the priority valve; when the guide oil is pushed from the left of the magnifying valve core to the right of the magnifying valve core, the pressure oil inlet and the left turning oil cylinder opening are gradually communicated by the magnifying valve and the priority valve. The present invention can be used by matching a proportioning pump, and not only has the function of magnifying flow rate but also can reduce the volume of an oil pump; the power loss and the cost of a hydraulic system can be reduced.
Description
Technical field
The present invention relates to the hydraulic transmission of engineering machinery, particularly a kind of priority-type flow rate enlarging and merging valve.
Background technique
Current engineering machinery is loader for example, the flux amplification valve that uses in its hydraulic steering system, the spool that is the guide oil control flow rate amplifying valve by small flow moves, flux amplification valve is entered with bigger flow turn to oil cylinder, and the guide oil of small flow becomes certain ratio with the big traffic steering working oil of flux amplification valve output, realizes the flow enlarging function.Owing to adopt metering pump, flow can not be regulated at any time, and the pressure-compensated valve in the flux amplification valve is only controlled pressure fuel pump and induced pressure keeps certain pressure reduction, and to guarantee the flow of priority of supply steering system, the unnecessary flow of its oil hydraulic pump returns fuel tank through pressure-compensated valve.The power consumpiton and the temperature elevation in hydraulic system of motor have so just been improved.A kind of solution is to adopt variable displacement pump, for example in the hydraulic steering system of loader, adopted variable displacement pump to add the flux amplification valve form, because the flow can regulate function of variable displacement pump, thereby make the output flow of pump realize that by the needs of reality flow is adjustable, the loss that makes output flow so seldom.Thereby realized power saving function, but because costing an arm and a leg of variable displacement pump reaches extremely instability of homemade variable displacement pump quality, loader industry does not at home almost adopt the variable displacement pump regulating system in steering hydraulic system at present.
Summary of the invention
The purpose of this invention is to provide a kind of priority-type flow rate enlarging and merging valve, it can cooperate metering pump to use, the function that existing flow amplifies, satisfy the requirement of engineering machinery steering operation, can reduce the work pump delivery again, thereby reduce the power loss of hydraulic system, reduce the cost of hydraulic system, and it is simple in structure, and is easily manufactured.
Priority-type flow rate enlarging and merging valve of the present invention is realized by following technological scheme.The feature of this priority-type flow rate enlarging and merging valve is: it comprises valve body, amplifying valve, pressure-gradient control valve, cone valve, shuttle valve, the left and right cylinder ports that turns on this valve all links to each other with cone valve through shuttle valve, when the guide oil that amplifies spool two ends all is cut off, cuts off this by priority spool and left and rightly turn to being connected of cylinder ports and pressure oil import; And pressure oil import and actuator port are interlinked by priority spool; When guide oil promotes from amplifying spool right left, by amplifying valve, pressure-gradient control valve pressure oil import and right steering cylinder ports are connected gradually, and left steering cylinder ports and return opening are connected, this moment, the oil of right steering cylinder ports affacted on the cone valve through shuttle valve; When guide oil from the left that amplifies spool during to right-hand promotion, by the amplifying valve pressure-gradient control valve pressure oil import and left steering cylinder ports are connected gradually, and right steering cylinder ports and return opening connected gradually, at this moment, the oil of left steering cylinder ports affacts on the cone valve through shuttle valve.The described mode of pressure oil import and right steering cylinder ports being connected gradually by amplifying valve is: crossing under ferry and the situation that the right steering cylinder ports is connected, pressure oil import and the connection mouth of crossing the ferry are strengthened gradually, reduce gradually by the connection mouth of priority spool simultaneously pressure oil import and actuator port; The described mode of pressure oil import and left steering oil cylinder being connected gradually by amplifying valve is: crossing under ferry and the situation that the left steering oil cylinder is connected, the pressure oil import is strengthened with mistake being connected gradually of ferry, reduce gradually by the connection mouth of priority spool simultaneously pressure oil import and working oil import.Its concrete structure is: described amplification spool and priority spool all are contained in the corresponding valve pocket of valve body, and constitute amplifying valve and pressure-gradient control valve with corresponding valve pocket, valve body comprises protecgulum and bonnet, in the right end chamber that amplifies spool spring is housed, the left and right end that amplifies spool all links to each other with guide's oil circuit through left and right guide's hydraulic fluid port; In the right end chamber of priority spool spring is housed, cone valve also is housed in this right end chamber, have radial hole in its left end chamber; On valve body,, have the left and right hydraulic fluid port that turns to corresponding to amplifying the valve pocket place, left and right sides return opening and cross the ferry, wherein, the left and right hydraulic fluid port that turns to all communicates with the right end chamber of priority spool through shuttle valve, by crossing the ferry preferential valve pocket and amplification valve pocket is interlinked; Cross the ferry and interlink, have the outer steerig pump of pressure hydraulic fluid port and valve in preferential valve pocket corresponding position and export and link to each other, also have actuator port and link to each other with the working oil pump discharge through radial hole and priority spool left end chamber; Respectively have connection mouth amplifying on spool and the priority spool, be positioned at each hydraulic fluid port on each valve pocket with connection.
The present invention finishes the flow enlarging function except adopting flux amplification valve of the prior art, it also installs the compensate function that pressure-gradient control valve has replaced the pressure-compensated valve in the prior art flux amplification valve additional by flux amplification valve, on the basis of the pressure compensation of finishing flux amplification valve, assurance turns to priority of supply, it turns to unnecessary flow to supply with hydraulic system of working by pressure-gradient control valve through the actuator port interflow, thereby not only reduced the oil mass of hydraulic system of working working pump, reduced the capacity of working pump, and reduced the power loss of hydraulic system, thereby improved the working efficiency of hydraulic system.Owing to do not use the metering pump of variable displacement pump and employing small capacity, greatly reduce the cost of hydraulic system yet.
In sum, the present invention has adopted flux amplification valve and pressure-gradient control valve structure combining, finish the flow enlarging function by flux amplification valve, guarantee outside the priority of supply steering flow by pressure-gradient control valve, with unnecessary flow is not to flow back to fuel tank by throttling, but be discharged to required hydraulic system of working by the pressure-gradient control valve interflow, as boom cylinder or rotary ink tank, reduced the power loss of hydraulic system, improve the working efficiency of hydraulic system, not only be suitable for the hydraulic system of metering pump, the cost of the hydraulic system of loader is reduced significantly, and because the interflow of loading machine steering system and hydraulic system of working is fully utilized flow rate of hydraulic system, improve the power utilization of this power engine effectively, saved the energy of loader hydraulic system.
Below in conjunction with accompanying drawing the present invention is done concrete introduction.
Description of drawings
Fig. 1 is a system diagram of the present invention,
Fig. 2 is a structural representation of the present invention.
Code name 1 protecgulum 2 amplifies spool among the figure, 2A amplifying valve 3 valve bodies 4 oilholes 5 springs 6 bonnets 7 pressure regulating screws 8 springs 9 cone valves 10 springs 11 oilholes 12 priority spools, 12A is preferential
Left and right hydraulic fluid port a, b, the left and right guide's hydraulic fluid port c radial hole P pressure hydraulic fluid port P1 pressure-gradient control valve left end chamber P2 pressure-gradient control valve right end chamber P3 transition PF actuator port T1 return opening of turning to of valve 13 shuttle valves 14,15 connection mouth A, B
Embodiment
As Fig. 1,2, the present invention includes valve body 3, amplifying valve 2A, pressure-gradient control valve 12A, cone valve 9, shuttle valve 13, described amplification spool 2 and priority spool 12 all are contained in the corresponding valve pocket of valve body 3, and constitute amplifying valve 2A and pressure-gradient control valve 12A with corresponding valve pocket, valve body 3 comprises protecgulum 1 and bonnet 6, in the right end chamber that amplifies spool 2 spring 5 is housed, the left and right end that amplifies spool 2 all links to each other with guide's oil circuit through left and right guide's hydraulic fluid port a, b; Spring 10 is housed in the right end chamber of priority spool 12, cone valve 9 also is housed in this right end chamber, have radial hole c in its left end chamber; On valve body 3 corresponding to amplifying the valve pocket place, have left and right hydraulic fluid port A, the B of turning to, left and right sides oil return inlet T 1 and mistake ferry P3, wherein, left and right hydraulic fluid port A, the B of turning to all communicates through the right end chamber of shuttle valve 13 with priority spool 12, by crossing ferry P3 preferential valve pocket and amplification valve pocket interlinked.Cross ferry P3 and interlink, have the outer steerig pump outlet of pressure hydraulic fluid port P and valve in preferential valve pocket corresponding position and link to each other, also have actuator port PF and link to each other with the oil pump oil circuit of working through radial hole C and priority spool 12 left end chamber P1; Respectively have connection mouth 14,15 amplifying on spool 2 and the priority spool 12, be positioned at each hydraulic fluid port on each valve pocket with connection.When using, following several situation can be arranged:
(1) neutral position
When the steering wheel stop rotated or redirect to extreme position, guide oil was cut off (promptly from a, the guide oil that the b direction enters the two ends, the left and right sides of amplifying spool 2 is cut off).Spring 5 makes and amplifies spool 2 and remain on the neutral position, has shut P3 → A (and B) mouthful, and the steering pump oil of coming can only enter P → P3 → C → P1 like this.Along with the pressure of P1 raises, the active force in P1 chamber increases gradually until greater than right-hand member spring 10 active forces (this moment, the pressure ratio in P2 chamber was lower).Priority spool 12 is moved to right, and P increases gradually to the opening of PF, satisfies to make the oil of steering pump all collaborate work system from the PF mouth, supplies with boom cylinder or rotary ink tank with working pump.Along with P when the opening of PF increases gradually, P reduces gradually to the opening of P3 but can not close.This is because pass through the oil circuit of P → P3 → C → P1, sets up the pressure in P1 chamber, and priority spool 12 is moved to right.Above-mentioned merging process is exactly the interflow function of priority spool 12.By the interflow effect discharge capacity of working pump is reduced, reduce outsourcing piece such as oil pump cost simultaneously, reduce temperature elevation in hydraulic system and power loss, improve the working efficiency of hydraulic system.
Owing to amplify the neutral position of spool 2, thus the hydraulic oil in P chamber with about turn to the hydraulic oil in hydraulic fluid port A, B chamber no longer to communicate, travel by rectilinear direction when the steering wheel stop of assurance loader turns to.Turn to the hydraulic oil in hydraulic fluid port A, B chamber to act on the cone valve 9 of safety valve by shuttle valve 13 about being enclosed in; when steered wheel is subjected to adding resistance; the pressure in A (or B) chamber raises up to opening cone valve 9 off-loads, turns to hydraulic element such as oil cylinder not to be destroyed with protection.
(2) right steering position
Bigger with respect to the guide oil of small flow from steering pump to the flow that turns to oil cylinder, and the guide oil of small flow becomes certain ratio with the flow of flux amplification valve output, owing to be the output that big flow is being controlled in the input of small flow, Here it is flow enlarging function.
When pressure oil flowed into right steering hydraulic fluid port B, because the load feedback effect remains unchanged the pressure difference that acts on priority spool 12 two ends substantially, thereby it was only irrelevant with the relevant and extraneous load of displacement of amplifying spool 2 to guarantee to remove to turn to the flow of oil cylinder.Turn to the pressure oil of hydraulic fluid port to enter the P2 chamber, act on the cone valve 9 of the right-hand member of priority spool 12 and safety valve, play the effect of automatic control flow by shuttle valve 13.If when steered wheel is subjected to adding resistance, the pressure in B chamber raises, and the pressure in P2 chamber is also along with rising so, and when surpassing set pressure for safety valve, cone valve 9 overcomes the pressure of spring 8, opens off-load, turns to hydraulic element such as oil cylinder not to be destroyed with protection.After load was eliminated, pressure reduced, and cone valve 9 cuts out and return to normal working.
Left steering is similar to right steering.
Claims (3)
1, priority-type flow rate enlarging and merging valve, it is characterized in that: it comprises valve body, amplifying valve, pressure-gradient control valve, cone valve, shuttle valve, the left and right cylinder ports that turns on this valve all links to each other with cone valve through shuttle valve, when the guide oil that amplifies spool two ends all is cut off, cuts off this by priority spool and left and rightly turn to being connected of cylinder ports and pressure oil import; And pressure oil import and actuator port are interlinked by priority spool; When guide oil promotes from amplifying spool right left, by amplifying valve, pressure-gradient control valve pressure oil import and right steering cylinder ports are connected gradually, and left steering cylinder ports and return opening connected gradually, this moment, the oil of right steering cylinder ports affacted on the cone valve through shuttle valve; When guide oil from the left that amplifies spool during to right-hand promotion, by the amplifying valve pressure-gradient control valve pressure oil import and left steering cylinder ports are connected gradually, and right steering cylinder ports and return opening connected gradually, at this moment, the oil of left steering cylinder ports affacts on the cone valve through shuttle valve.
2, priority-type flow rate enlarging and merging valve according to claim 1, it is characterized in that: the described mode of pressure oil import and right steering cylinder ports being connected gradually by amplifying valve is: crossing under ferry and the situation that the right steering cylinder ports is connected, pressure oil import and the connection mouth of crossing the ferry are strengthened gradually, reduce gradually by the connection mouth of priority spool simultaneously pressure oil import and actuator port; The described mode of pressure oil import and left steering oil cylinder being connected gradually by amplifying valve is: crossing under ferry and the situation that the left steering oil cylinder is connected, pressure oil import and the connection mouth of crossing the ferry are strengthened gradually, reduce gradually by the connection mouth of priority spool simultaneously pressure oil import and working oil import.
3, priority-type flow rate enlarging and merging valve according to claim 1 and 2, it is characterized in that: described amplification spool (2) and priority spool (12) all are contained in the corresponding valve pocket of valve body (3), and constitute amplifying valve (2A) and pressure-gradient control valve (12A) with corresponding valve pocket, valve body (3) comprises protecgulum (1) and bonnet (6), in the right end chamber that amplifies spool (2) spring (5) is housed, the left and right end that amplifies spool (2) all links to each other with guide's oil circuit through left and right guide's hydraulic fluid port (a) and (b); Spring (10) is housed in the right end chamber of priority spool (12), cone valve (9) also is housed in this right end chamber, have radial hole (c) in its left end chamber; Go up corresponding to amplifying the valve pocket place at valve body (3), have left and right hydraulic fluid port (A), (B) of turning to, left and right sides return opening (T1) and mistake ferry (P3), wherein, left and right hydraulic fluid port (A), (B) of turning to all communicates through the right end chamber of shuttle valve (13) with priority spool (12), by crossing ferry (P3) preferential valve pocket and amplification valve pocket interlinked; Cross ferry (P3) and interlink, have the outer steerig pump of pressure hydraulic fluid port (P) and valve in preferential valve pocket corresponding position and export and link to each other, also have actuator port (PF) and link to each other with the working oil pump discharge through radial hole (C) and priority spool (12) left end chamber (P1); Respectively have connection mouth (14), (15) amplifying on spool (2) and the priority spool (12), be positioned at each hydraulic fluid port on each valve pocket with connection.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB001362429A CN1136397C (en) | 2000-12-28 | 2000-12-28 | Priority-type flow rate enlarging and merging valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB001362429A CN1136397C (en) | 2000-12-28 | 2000-12-28 | Priority-type flow rate enlarging and merging valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1361362A CN1361362A (en) | 2002-07-31 |
| CN1136397C true CN1136397C (en) | 2004-01-28 |
Family
ID=4597162
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB001362429A Expired - Fee Related CN1136397C (en) | 2000-12-28 | 2000-12-28 | Priority-type flow rate enlarging and merging valve |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1136397C (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102003425B (en) * | 2010-11-29 | 2014-05-07 | 广西玉柴重工有限公司 | Priority valve for hydraulic excavator |
| CN102734245B (en) * | 2012-07-06 | 2015-05-27 | 浙江海克力液压有限公司 | Preferential-type variable steering control valve |
| CN105114381B (en) * | 2015-07-27 | 2017-03-01 | 浙江海宏液压科技股份有限公司 | Interflow banked direction control valves |
| CN105626615A (en) * | 2016-02-29 | 2016-06-01 | 浙江高宇液压机电有限公司 | Steering feedback type flow amplification valve |
| CN107489670A (en) * | 2017-09-11 | 2017-12-19 | 雷沃重工股份有限公司 | A kind of flow divider block |
| CN114576228B (en) * | 2022-05-06 | 2022-07-22 | 英轩重工有限公司 | Flow amplifying valve and steering hydraulic control system thereof |
-
2000
- 2000-12-28 CN CNB001362429A patent/CN1136397C/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| CN1361362A (en) | 2002-07-31 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN106759621B (en) | Load-sensitive formula loading machine determines variable delivery hydraulic system | |
| CN105134695A (en) | Electric control opening and closing core hydraulic system and engineering machine | |
| CN202251199U (en) | Electro-hydraulic proportional combined maneuvering valve | |
| CN204985186U (en) | Automatically controlled switching core hydraulic system and engineering machinery | |
| CN204164074U (en) | Multi-way valve and hydraulic flow shared system | |
| CN105570220A (en) | Multiway valve and hydraulic flow sharing system | |
| CN105134678A (en) | Pilot control valve block, core opening and closing hydraulic system and engineering machine | |
| CN103267147A (en) | Small-flow high-pressure load sensitive proportional multi-way valve | |
| CN111255007B (en) | Loader constant-variable hydraulic system based on load signal direct control | |
| CN102991571B (en) | Hydraulic control loop, hydraulic control system and hydraulic control valve group | |
| CN105402182B (en) | Load sensing multiple directional control valve and loader hydraulic control system | |
| CN203297181U (en) | load sensing system | |
| CN1136397C (en) | Priority-type flow rate enlarging and merging valve | |
| CN113494111B (en) | Main control valve, fixed variable hydraulic system and loader | |
| CN113482090B (en) | Main control valve, constant-variable hydraulic system and loader | |
| CN113431127A (en) | Main control valve, fixed variable hydraulic system and loader | |
| CN115489593A (en) | Steering flow control valve, hydraulic steering system and wheeled traveling apparatus | |
| CN106762903B (en) | Multiple directional control valve | |
| CN204985130U (en) | Pilot control valve piece, switching core hydraulic system and engineering machinery | |
| CN209875588U (en) | Oil source valve, hydraulic system and engineering machinery | |
| CN112879370B (en) | Balance adjustment hydraulic valve set for farm tool | |
| CN2505632Y (en) | Pilot-controlled multi-way reversing valve | |
| CN110985458B (en) | Multistage differential pressure control hydraulic system | |
| CN110578726B (en) | Quantitative system variable hydraulic system | |
| CN111720376A (en) | Flow dividing valve, hydraulic system thereof and engineering machinery |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C06 | Publication | ||
| PB01 | Publication | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C19 | Lapse of patent right due to non-payment of the annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |