CN102913438A - Hydraulic pump changeover valve - Google Patents
Hydraulic pump changeover valve Download PDFInfo
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- CN102913438A CN102913438A CN201110223514XA CN201110223514A CN102913438A CN 102913438 A CN102913438 A CN 102913438A CN 201110223514X A CN201110223514X A CN 201110223514XA CN 201110223514 A CN201110223514 A CN 201110223514A CN 102913438 A CN102913438 A CN 102913438A
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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 oil hydraulic pump changing valve, it can be transformed to metering pump with oil pump load-sensing and that the variable displacement pump function is arranged, so that working load induction technology and proportional control technology belong to technical field of hydraulic.
Background technique
In the hydraulic system of movable type mechanical, in order to improve the efficient of hydraulic system, save energy and improve operating characteristics, usually adopt the variable displacement pump of bringing onto load induction.And the cost of variable displacement pump is in the situation that same flow is the several times of metering pump or tens times, because cost is too high, this has brought very large difficulty for hydraulic system of middle small flow, and causing can't working load induction technology and pressure compensated proportional control technology.This also is the seldom main cause of working load induction technology and proportional control technology of present medial and small construction machinery, farm machinery and building machinery.
Summary of the invention
In order to allow medial and small construction machinery, farm machinery and the building machinery can working load induction technology and proportional control technology, the invention provides a kind of oil hydraulic pump changing valve.
Proportional control and proportional diverting control.The technical solution used in the present invention is: the valve body that comprises the oil hydraulic pump conversion, filler opening, auxiliary oil channel, the throttling spool groove, spool, the throttle orifice screw, seal ring, plug, outer spring, auxiliary plug, inner spring, pad, the valve core inside passage, drainback passage, the oil return connection mouth, the oil return connecting passage, the oil-feed connection mouth, return opening, oilhole, the annular drainback passage, the hydro-cushion groove, the load-sensing circular groove, the load-sensing wedgy passage, the plug hole, plug, impedance screw, the load-sensing relief valve, the induction channels interface that leads to work connection pressure compensator, the load-sensing attachment hole, the load-sensing plug, the interface that leads to the shuttle valve system, the load-sensing joint, the relief valve drainback passage, the oil hydraulic pump changing valve, multi-way valve work connection, the spring oil pocket, the oil-feed oil duct, the multi-way valve rear end cover.The filler opening of oil hydraulic pump changing valve connects the oil outlet of metering pump among the present invention by high pressure hose or high-pressure oil pipe, the diverse location of the spool by the pressure difference controller decides the uninterrupted of supply system, and remaining fluid flows back to fuel tank via the restriction of spool.One end of pressure difference controller spool bears input pressure, and the other end bears the pressure from the load-sensing oil circuit, and the difference of the pressure at their two ends is that the spring force by two springs comes balance.Change the pretightening force of spring, just can change the pressure loss of system.Pressure difference controller spool is a columniform spool, also hollow spool.Have throttling groove at spool, be used for when opening, fluid being connected to fuel tank.The size of the flow area of spool open place and input pressure determine to be discharged to the uninterrupted of fuel tank.
Different from common load-sensing, the oil hydraulic pump changing valve adopts the double loop loop inductance.The load-sensing pressure of spring chamber be each connection in the Multigang valve system induced pressure through the shuttle valve comparison system relatively after, maximum load pressure more out.Maximum load pressure converged behind a throttle orifice with each pressure that joins the spring chamber of pressure compensator before the arrival throttle orifice.Such load-sensing connecting mode has improved Systems balanth greatly.
In the load-sensing loop, for the pressure maximum of restriction system, the relief valve of a small flow is housed.In case the induced pressure of system reaches the set pressure of relief valve, relief valve is opened, and load-sensing pressure just can not rise again, and at this moment oil pump goes out the namely pressure maximum of system of oil pressure.
This device is designed to the oil-feed connection of Multigang valve, is associated with identical interface with the work of Multigang valve.The output of metering pump is connected to the import of this device.This device inside is provided with pressure difference controller and load-sensing passage, in order to arrive system to the demand of flow by the load-sensing pressure sensitive.The outlet pressure of pressure difference controller control oil pump and load-sensing pressure poor makes it be tending towards a normal value.When system did not have traffic demand, load-sensing pressure was very low, is tending towards tank pressure, and whole flows of metering pump flow to fuel tank through unloading port, and system consumes lower-wattage with low pressure (10 to 14bar) running.When there was traffic demand in system, load-sensing pressure raise, and to the system output stream amount, unnecessary flow flows to fuel tank from the restriction of spool to interface according to the needs of system.The outlet pressure of oil pump is the summation of the pressure reduction of load-sensing pressure and differential pressure controller.After having used this multi-way valve interface, system just can use the control technique of any multi-way valve, as: bringing onto load is responded to, band pressure compensation
Description of drawings
Below in conjunction with accompanying drawing the present invention is further specified.
Fig. 1 is the 3 dimensional drawing of oil hydraulic pump changing valve of the present invention
Fig. 2 is the plan view of oil hydraulic pump changing valve of the present invention
Fig. 3 be in the accompanying drawing 2 G-G to view
Fig. 4 is the spool 3 dimensional drawing of oil hydraulic pump changing valve of the present invention
Fig. 5 be in the accompanying drawing 3 K-K to view
Fig. 6 be in the accompanying drawing 4 L-L to view
Fig. 7 is the enforcement illustration of oil hydraulic pump changing valve of the present invention
In the accompanying drawing: the valve body of 1 oil hydraulic pump conversion, 2, filler opening, 3 auxiliary oil channels, 4 throttling spool grooves, 5 spools, 6 throttle orifice screws, 7 seal rings, 8 plugs, 9 outer springs, 10 auxiliary plugs, 11 inner springs, 12 pads, 13 valve core inside passages, 14 drainback passages, 15 oil return connection mouths, 16 oil return connecting passages, 17 oil-feed connection mouths, 18 return openings, 19 oilholes, 20 annular drainback passages, 21 hydro-cushion grooves, 22 load-sensing circular grooves, 23 load-sensing wedgy passages, 24 plug holes, 25 plugs, 26 impedance screws, 27 load-sensing relief valves, 28 lead to the induction channels interface of work connection pressure compensator, 29 load-sensing attachment holes, 30 load-sensing plugs, 31 lead to the interface of shuttle valve system, 32 load-sensing joints, 33 relief valve drainback passages, 34 oil hydraulic pump changing valves, 35 multi-way valve work connection, 36 spring oil pockets, 37 oil-feed oil ducts, 38 multi-way valve rear end covers.
Embodiment
In Fig. 1,2,3,4, the valve body of oil hydraulic pump changing valve (1) is cast with oil-feed oil duct (37) and auxiliary oil channel (3).Oil-feed oil duct (37) extends to oil-feed connection mouth (17) always, and this connection mouth connects the oil inlet passage of each work connection of multi-way valve.Auxiliary oil channel (3) is guide's oil circuit fuel feeding.The fluid of metering pump output arrives oil-feed oil duct (37) through filler opening (2).The oil pressure of oil-feed oil duct (37) acts on an end of spool (5), and the other end of spool (5) bears the oil pressure of spring oil pocket (36) and the spring force of outer spring (9) and inner spring (11).That is to say, the difference of the pressure at spool (5) two ends is to come balance by spring force.The fluid of oil-feed oil duct (2) can pass through oilhole (19) is connected 13 with the valve core inside passage) be connected 36 through the throttle orifice of impedance screw (6) with the spring oil pocket) connect.Visible system needs, and impedance screw (6) can be provided with throttle orifice, also can not establish throttle orifice.Spool (5) upper in addition throttling groove (4) and relief groove (21).The valve body of oil hydraulic pump changing valve (1) also is cast with drainback passage (14), oil return connecting passage (16) and annular drainback passage (20).Oil return connecting passage (16) connects two oil return connection mouths (15), and annular drainback passage (20) connects return opening (18).Two oil return connection mouths (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 circular groove (22).Spring oil pocket (36) communicates with load-sensing wedgy passage (23) through load-sensing circular groove (22).Load-sensing wedgy passage (23) communicates with the plug hole (24) of plug (25) again.The fluid of the load-sensing that is come through the shuttle valve system by multi-way valve work connection (35) the again fluid of the interface (31) through leading to the shuttle valve system and the induction channels interface (28) that leads to work connection pressure compensator converges, and is communicated to the import of the throttle orifice of load-sensing relief valve (27) and impedance screw (26) after converging by load-sensing connecting passage (29) again.When load-sensing pressure during greater than the setting of load-sensing relief valve (27), load-sensing relief valve (27) is opened, load-sensing fluid through the restriction of relief valve again through relief valve drainback passage (33) oil sump tank.Load-sensing fluid is connected with plug hole (24) through the throttle orifice of impedance screw (26), communicates with spring oil pocket (36) through load-sensing wedgy passage (23) and load-sensing circular groove (22) again.Therefore, load-sensing pressure is transferred to the spring chamber of spool (5).One end of load-sensing attachment hole (29) is blocked by load-sensing plug (30).
Claims (3)
1. oil hydraulic pump changing valve, the valve body that comprises the oil hydraulic pump conversion, filler opening, auxiliary oil channel, the throttling spool groove, spool, the throttle orifice screw, seal ring, plug, outer spring, auxiliary plug, inner spring, pad, the valve core inside passage, drainback passage, the oil return connection mouth, the oil return connecting passage, the oil-feed connection mouth, return opening, oilhole, the annular drainback passage, the hydro-cushion groove, the load-sensing circular groove, the load-sensing wedgy passage, the plug hole, plug, impedance screw, the load-sensing relief valve, the induction channels interface that leads to work connection pressure compensator, the load-sensing attachment hole, the load-sensing plug, the interface that leads to the shuttle valve system, the load-sensing joint, the relief valve drainback passage, the oil hydraulic pump changing valve, multi-way valve work connection, the spring oil pocket, the oil-feed oil duct, the multi-way valve rear end cover, it is characterized in that being provided with in the valve body pressure difference controller, oil inlet passage is in throttling groove one side of spool in the valve body, the load-sensing passage is at the opposite side of spool, this side is equipped with spring, the spring chamber front end is provided with a throttle orifice, and the load-sensing pressure of system is the pressure maximum through the system load more out of shuttle valve comparison system.
2. a kind of oil hydraulic pump changing valve according to claim 1 is characterized in that oil-feed connection and Multigang valve valve body that it both can make a Multigang valve match, and same oil circuit interface is arranged, also can make one independently valve be connected with control valve with pipeline.
3. a kind of oil hydraulic pump changing valve according to claim 1 is characterized in that its spool is by a circular spool, spring, and plug, sealing and corresponding valve channel form; Have throttling groove on the step of circular spool, in a side of minor diameter radial hole and axial bore are arranged, by a throttle orifice (damping hole) oil inlet passage and load-sensing oil pocket are connected, also can block.
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 true CN102913438A (en) | 2013-02-06 |
| CN102913438B CN102913438B (en) | 2017-02-08 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201110223514.XA Active CN102913438B (en) | 2011-08-05 | 2011-08-05 | Hydraulic pump changeover valve |
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| CN (1) | CN102913438B (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105840573A (en) * | 2015-01-16 | 2016-08-10 | 徐工集团工程机械股份有限公司 | Valve body of first link of load-sensitive multi-way valve and first link of load-sensitive multi-way valve |
| CN105952630A (en) * | 2016-06-21 | 2016-09-21 | 珠海格力电器股份有限公司 | Hydraulic pump and air conditioner |
| CN110761987A (en) * | 2019-10-25 | 2020-02-07 | 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 (8)
| 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 |
| JPH1113705A (en) * | 1997-06-20 | 1999-01-22 | Zexel Corp | Hydraulic control valve device |
| 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 |
-
2011
- 2011-08-05 CN CN201110223514.XA patent/CN102913438B/en active Active
Patent Citations (8)
| 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 |
| JPH1113705A (en) * | 1997-06-20 | 1999-01-22 | Zexel Corp | Hydraulic control valve device |
| 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 |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105840573A (en) * | 2015-01-16 | 2016-08-10 | 徐工集团工程机械股份有限公司 | Valve body of first link of load-sensitive multi-way valve and first link of load-sensitive multi-way valve |
| CN105952630A (en) * | 2016-06-21 | 2016-09-21 | 珠海格力电器股份有限公司 | Hydraulic pump and air conditioner |
| 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 |
| CN110761987A (en) * | 2019-10-25 | 2020-02-07 | 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 |
| 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 |
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| CN102913438B (en) | 2017-02-08 |
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