CN102913438B - Hydraulic pump changeover valve - Google Patents
Hydraulic pump changeover valve Download PDFInfo
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- CN102913438B CN102913438B CN201110223514.XA CN201110223514A CN102913438B CN 102913438 B CN102913438 B CN 102913438B CN 201110223514 A CN201110223514 A CN 201110223514A CN 102913438 B CN102913438 B CN 102913438B
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Abstract
The invention relates to a hydraulic pump changeover valve, which can convert a fixed displacement pump into an oil pump with a load sensing function and a function of a variable displacement pump. The hydraulic pump changeover valve comprises a valve body, a dynamic sensing valve core, a spring and the like, wherein the valve body is connected with a connector plane of a main valve block of a multi-way valve; the top end of the valve body is provided with an oil inlet, an oil return port, a prior circuit oil port, a prior circuit load sensing oil port and a system load sensing oil port; and a wedge-shaped channel is casted in the valve body. The hydraulic pump changeover valve can be designed in a manner that an oil inlet union of a multi-union valve is matched with a valve body of the multi-union valve and the same oil circuit connector is provided, and can be further designed in a manner that an independent valve pipe is connected with a control valve, so that the priority can be provided, the structure of the multi-way valve is greatly simplified, the cost is saved at the same time, and the hydraulic pump changeover valve has good stability.
Description
Technical field
The present invention relates to a kind of hydraulic pump changeover valve, it can by dosing pump be transformed to load-sensing and have variable pump
The oil pump of function, to use load-sensing technology and proportional control technique, belongs to technical field of hydraulic.
Background technology
In the hydraulic system of movable type mechanical, in order to improve the efficiency of hydraulic system, save energy expenditure and improve behaviour
Make performance, usually adopt the variable pump of bringing onto load sensing.And the cost of variable pump is dosing pump in the case of same flow
Several times or more than ten times, because cost is too high, this brings very big difficulty to the hydraulic system of medium-small flow, leads to not use
Load-sensing technology and pressure compensated proportional control technique.This is also current medial and small construction machinery, agricultural machinery and builds
Build machinery and be rarely employed load-sensing technology and the main cause of proportional control technique.
Content of the invention
In order to allow medial and small construction machinery, agricultural machinery and building machinery can use load-sensing technology and ratio
Control technology, the invention provides a kind of hydraulic pump changeover valve.
The technical solution used in the present invention is：Including the valve body of hydraulic pump changeover valve, oil-in, auxiliary oil channel, valve element section
Chute, valve element, throttle orifice screw, sealing ring, valve element plug, outer spring, auxiliary plug, inner spring, pad, valve core inside lead to
Road, drainback passage, oil return connector, oil return interface channel, oil-feed connector, oil return opening, oilhole, annular drainback passage, hydraulic pressure
Compensating groove, load-sensing cannelure, load-sensing wedgy passage, plug hole, plug, impedance screw, load-sensing overflow valve, logical
Toward the induction channels interface joining pressure compensator that works, load-sensing connecting hole, load-sensing plug, lead to connecing of shuttle valve system
Mouth, load-sensing joint, overflow valve drainback passage, hydraulic pump changeover valve, banked direction control valves work connection, spring oil pocket, oil-feed oil duct,
Banked direction control valves rear end cap.In the present invention, the oil-in of hydraulic pump changeover valve passes through high-pressure hose or high-pressure oil pipe connects going out of dosing pump
Hydraulic fluid port, determines the uninterrupted of feed system by the diverse location of the valve element of pressure difference controller, remaining fluid via
The restriction of valve element flows back to fuel tank.Input pressure is born in one end of pressure difference controller valve element, and the other end bears self-supported sense
Answer the pressure of oil circuit, the difference of the pressure at their two ends is to be balanced by the spring force of two springs.Change the pretightning force of spring, just
The pressure loss of system can be changed.Pressure difference controller valve element is a cylindrical valve element, may also be hollow spool.In valve
Throttling channel is had on core, for fluid being connected to fuel tank when opening.The size of the flow area of valve element open place and oil-feed
Pressure determines to be discharged to the uninterrupted of fuel tank.
Different from common load-sensing, hydraulic pump changeover valve adopts double loop loop inductance.Load sense in spring cavity
Answer pressure be each load pressure in multi-joint valve system through shuttle valve comparison system relatively after, the maximum comparing out is born
Carry pressure.Maximum load pressure before reaching throttle orifice with the pressure of the spring cavity of each pressure compensator through a throttle orifice
After converge.Such load-sensing connecting mode substantially increases the stability of system.
In load-sensing loop, in order to limit the maximum pressure of system, equipped with the overflow valve of a low discharge.Once being
The load pressure of system reaches the set pressure of overflow valve, and overflow valve is opened, load-sensing pressure would not rise again, at this moment pump
Go out the maximum pressure of oil pressure i.e. system.
This device is designed to the oil-feed connection of Multigang valve, and the work with Multigang valve is associated with identical interface.By dosing pump
Output is connected to the import of this device.It is provided with pressure difference controller and load-sensing passage inside this device, negative will pass through
Carry induction pressure and sense the demand to flow for the system.The outlet pressure of pressure difference controller control oil pump and load-sensing pressure
Difference so as to tend to a constant value.When system does not have traffic demand, load-sensing pressure is very low, tends to tank pressure, quantitative
Whole flows of pump flow to fuel tank through unloading port, and system is operated with low pressure (10 to 14bar), consume lower-wattage.Have in system
During traffic demand, load-sensing pressure rise, according to the needs of system to system output stream amount, excess traffic is from valve element for interface
Restriction flows to fuel tank.The outlet pressure of oil pump is the summation of the pressure reduction of load-sensing pressure and differential pressure controller.Employ this
After individual banked direction control valves interface, system can be with the control technology using any banked direction control valves, such as：Bringing onto load sensing, band pressure compensation
Brief description
Below in conjunction with the accompanying drawings the present invention is further described
Fig. 1 is the 3 dimensional drawing of hydraulic pump changeover valve of the present invention
Fig. 2 is the top view of hydraulic pump changeover valve of the present invention
Fig. 3 is in accompanying drawing 2 ' G-G direction view
Fig. 4 is the valve element 3 D stereo of hydraulic pump changeover valve of the present invention
Fig. 5 is K-K direction view in accompanying drawing 3
Fig. 6 is L-L direction view in accompanying drawing 5
Fig. 7 is the enforcement illustration of hydraulic pump changeover valve of the present invention
In accompanying drawing：The valve body of 1 hydraulic pump changeover valve, 2, oil-in, 3 auxiliary oil channels, 4 throttling spool grooves, 5 valve elements, 6 throttling
Hole screw, 7 sealing rings, 8 valve element plugs, 9 outer springs, 10 auxiliary plugs, 11 inner springs, 12 pads, 13 valve core inside passages, 14
Drainback passage, 15 oil return connectors, 16 oil return interface channels, 17 oil-feed connectors, 18 oil return openings, 19 oilholes, 20 annular oil returns
Passage, 21 hydro-cushion grooves, 22 load-sensing cannelures, 23 load-sensing wedgy passages, 24 plug holes, 25 plugs, 26 throttlings
Screw, 27 load-sensing overflow valves, 28 lead to work join the induction channels interface of pressure compensator, 29 load-sensing connecting holes,
30 load-sensing plugs, 31 lead to the interface of shuttle valve system, 32 load-sensing joints, 33 overflow valve drainback passages, 34 hydraulic pressure
Pump switching valve, 35 banked direction control valves work connection, 36 spring oil pockets, 37 oil-feed oil ducts, 38 banked direction control valves rear end caps.
Specific embodiment
In Fig. 1,2,3,4, the valve body (1) of hydraulic pump changeover valve is cast with oil-feed oil duct (37) and auxiliary oil channel (3).Oil-feed
Oil duct (37) extends to oil-feed connector (17), and this connector connects the oil inlet passage of banked direction control valves each work connection.Auxiliary
Oil duct (3) is guide's oil circuit fuel feeding.The fluid of dosing pump output arrives oil-feed oil duct (37) through oil-in (2).Oil-feed oil duct (37)
Oil pressure act on one end of valve element (5), the other end of valve element (5) bears oil pressure and the outer spring of spring oil pocket (36)
(9) spring force with inner spring (11).That is, the difference of the pressure at valve element (5) two ends is to be balanced by spring force.Oil-feed oil
The fluid in road (2) can be by oilhole (19) and valve core inside passage (13) throttle orifice through impedance screw (6) and spring oil pocket
(36) connect.Visible system needs, and impedance screw (6) can be provided with throttle orifice it is also possible to not set throttle orifice.Valve element (5) is upper to be also had
Throttling channel (4) and relief groove (21).The valve body (1) of hydraulic pump changeover valve is also cast with drainback passage (14), oil return connects and leads to
Road (16) and annular drainback passage (20).Oil return interface channel (16) connects two oil return connectors (15), annular drainback passage
(20) connect oil return opening (18).Two oil return connectors (15) connect two drainback passages of Multigang valve.
In Fig. 5, Fig. 6, valve body (1) is cast with load-sensing wedgy passage (23) and load-sensing cannelure (22).Spring
Oil pocket (36) is communicated with load-sensing wedgy passage (23) through load-sensing cannelure (22).Load-sensing wedgy passage (23) and
Communicate with the plug hole (24) of plug (25).The fluid warp again of the load-sensing being come through shuttle valve system by banked direction control valves work connection (35)
Interface (31) towards shuttle valve system is converged with the fluid of the induction channels interface (28) joining pressure compensator towards work, converges
It is communicated to the import of the throttle orifice of load-sensing overflow valve (27) and impedance screw (26) afterwards again by load-sensing connecting hole (29).
When load-sensing pressure is more than the setting of load-sensing overflow valve (27), load-sensing overflow valve (27) is opened, load sense
Answer the restriction through overflow valve for the fluid again through overflow valve drainback passage (33) oil sump tank.Load-sensing fluid is through impedance screw (26)
Throttle orifice be connected with plug hole (24), then through load-sensing wedgy passage (23) and load-sensing cannelure (22) and spring oil
Chamber (36) communicates.Therefore, load-sensing pressure is transferred to the spring cavity of valve element (5).One end quilt of load-sensing connecting hole (29)
Load-sensing plug (30) blocks.
Claims (1)
1. a kind of hydraulic pump changeover valve, including the valve body of hydraulic pump changeover valve, oil-in, auxiliary oil channel, throttling spool groove, valve
Core, throttle orifice screw, sealing ring, valve element plug, auxiliary plug, pad, valve core inside passage, drainback passage, oil return connector,
Oil return interface channel, oil-feed connector, oil return opening, oilhole, annular drainback passage, hydro-cushion groove, load-sensing cannelure, negative
Carry sensing wedgy passage, plug hole, plug, impedance screw, load-sensing overflow valve, lead to the sensing that work joins pressure compensator
Channel interface, load-sensing connecting hole, load-sensing plug, the interface leading to shuttle valve system, load-sensing joint, overflow valve
Drainback passage, banked direction control valves work connection, spring cavity, oil-feed oil duct, banked direction control valves rear end cap；
The valve body of hydraulic pump changeover valve is cast with oil-feed oil duct and auxiliary oil channel；Oil-feed oil duct extends to oil-feed connector, should
Connector connects the oil-feed oil duct of banked direction control valves each work connection；
The valve body of hydraulic pump changeover valve is also cast with drainback passage, oil return interface channel and annular drainback passage；Oil return interface channel
Connect two oil return connectors, annular drainback passage connects oil return opening；Two oil return connectors connect two oil returns of Multigang valve
Passage,
It is characterized in that being provided with a pressure difference controller in valve body, in valve body, oil-feed oil duct, in the throttling channel side of valve element, is born
Carry the opposite side in valve element for the sensing wedgy passage, equipped with spring, described spring is made up of outer spring and inner spring, spring cavity for this side
Front end is provided with a throttle orifice, the load-sensing pressure of system be the system load comparing out through shuttle valve comparison system
Big pressure；
Valve body is cast with load-sensing wedgy passage and load-sensing cannelure, and spring cavity is through load-sensing cannelure and load-sensing
Wedgy passage communicates, and load-sensing wedgy passage is communicated with the plug hole of plug again；Come through shuttle valve system by banked direction control valves work connection
Load-sensing fluid again through towards the interface of shuttle valve system and the induction channels interface joining pressure compensator towards work
Fluid converges, and is communicated to entering of the throttle orifice of load-sensing overflow valve and impedance screw by load-sensing connecting hole again after converging
Mouthful.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201110223514.XA CN102913438B (en) | 2011-08-05 | 2011-08-05 | Hydraulic pump changeover valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201110223514.XA CN102913438B (en) | 2011-08-05 | 2011-08-05 | Hydraulic pump changeover valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102913438A CN102913438A (en) | 2013-02-06 |
| CN102913438B true CN102913438B (en) | 2017-02-08 |
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ID=47611954
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201110223514.XA Active CN102913438B (en) | 2011-08-05 | 2011-08-05 | Hydraulic pump changeover valve |
Country Status (1)
| Country | Link |
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| CN (1) | CN102913438B (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105840573B (en) * | 2015-01-16 | 2018-04-06 | 徐工集团工程机械股份有限公司 | Load sensing multi-way valve first valve body and load sensing multi-way valve first |
| CN105952630B (en) * | 2016-06-21 | 2019-11-22 | 珠海格力电器股份有限公司 | Hydraulic pump and air conditioner |
| CN110761987B (en) * | 2019-10-25 | 2021-09-10 | 苏师大半导体材料与设备研究院(邳州)有限公司 | Ceramic slurry pump medium distribution mechanism |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4688600A (en) * | 1985-02-28 | 1987-08-25 | Mannesmann Rexroth Gmbh | Multiway valve with pressure balance |
| GB2271625A (en) * | 1992-10-19 | 1994-04-20 | Dana Corp | Post-pressure compensated spool valve |
| US5454223A (en) * | 1993-05-28 | 1995-10-03 | Dana Corporation | Hydraulic load sensing system with poppet valve having an orifice therein |
| US5715865A (en) * | 1996-11-13 | 1998-02-10 | Husco International, Inc. | Pressure compensating hydraulic control valve system |
| CN201443544U (en) * | 2009-04-16 | 2010-04-28 | 山推工程机械股份有限公司传动分公司 | Multichannel hydraulic control valve used for prorating load flow |
| CN101929481A (en) * | 2010-04-30 | 2010-12-29 | 北京联合大学 | Three-way pressure compensating valve for hydraulic energy-saving system |
| CN102141062A (en) * | 2011-02-25 | 2011-08-03 | 江苏国瑞液压机械有限公司 | Proportion distribution dual induction and dual damping pressure compensator |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH1113705A (en) * | 1997-06-20 | 1999-01-22 | Zexel Corp | Hydraulic control valve device |
-
2011
- 2011-08-05 CN CN201110223514.XA patent/CN102913438B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4688600A (en) * | 1985-02-28 | 1987-08-25 | Mannesmann Rexroth Gmbh | Multiway valve with pressure balance |
| GB2271625A (en) * | 1992-10-19 | 1994-04-20 | Dana Corp | Post-pressure compensated spool valve |
| US5454223A (en) * | 1993-05-28 | 1995-10-03 | Dana Corporation | Hydraulic load sensing system with poppet valve having an orifice therein |
| US5715865A (en) * | 1996-11-13 | 1998-02-10 | Husco International, Inc. | Pressure compensating hydraulic control valve system |
| CN201443544U (en) * | 2009-04-16 | 2010-04-28 | 山推工程机械股份有限公司传动分公司 | Multichannel hydraulic control valve used for prorating load flow |
| CN101929481A (en) * | 2010-04-30 | 2010-12-29 | 北京联合大学 | Three-way pressure compensating valve for hydraulic energy-saving system |
| CN102141062A (en) * | 2011-02-25 | 2011-08-03 | 江苏国瑞液压机械有限公司 | Proportion distribution dual induction and dual damping pressure compensator |
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| Publication number | Publication date |
|---|---|
| CN102913438A (en) | 2013-02-06 |
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