CN201443544U - Multichannel hydraulic control valve used for prorating load flow - Google Patents
Multichannel hydraulic control valve used for prorating load flow Download PDFInfo
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- CN201443544U CN201443544U CN2009200212512U CN200920021251U CN201443544U CN 201443544 U CN201443544 U CN 201443544U CN 2009200212512 U CN2009200212512 U CN 2009200212512U CN 200920021251 U CN200920021251 U CN 200920021251U CN 201443544 U CN201443544 U CN 201443544U
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Abstract
The utility model relates to a multichannel hydraulic control valve used for prorating load flow, in particular to multichannel hydraulic control valve equipment used for a small-sized excavator. The multichannel hydraulic control valve is connected to a screwed hole of an oil inlet valve through one end of a stud bolt, the other end of the stud bolt is tightly connected together with a nut, an oil inlet is communicated with an oil inlet channel, an oil return port is communicated with two oil return channels, and a load induction oil port is communicated with a load induction oil channel; and an unloading valve spring is arranged between an unloading valve cap and an unloading valve core. A safety valve, an overflow valve and a throttle valve are screw-thread cartridge valves, a reversal valve core is arranged in a valve-core hole of a reversal valve body, a variable throttle valve is arranged on the reversal valve core, a pressure-compensated valve moves up and down inside a load induction cavity, and the upper end of the load induction cavity is communicated with the load induction oil channel. The utility model has the effects of simple structure, convenient operation, no load interference phenomenon, composite actions, and multiple actuator supply by a single pump, and is widely applied to the multichannel hydraulic control valve in a hydraulic-pressure transmission system of the small-sized excavator.
Description
Technical field:
The utility model relates to a kind of load flow pro rate multipath hydraulic control valve, especially for the load flow pro rate multipath hydraulic control valve equipment in the mini-excavator Hydraulic Power Transmission System.
Background technique:
At present, the hydraulic control system of multifunctional engineering machineries such as hydraulic shovel generally adopts the multipath hydraulic control valve, realizes exercises by multipath hydraulic control valve Control work device, walking, rotation oil; The performance of multipath hydraulic control valve directly influences the technical performance of engineering machinery, the multipath hydraulic control valve that is used for the small crawler hydraulic shovel generally is the open circuit structure that adopts six logical multipath hydraulic control valves, its shortcoming is the influence that governor control characteristics is subjected to induced pressure and oil pump flow, speed adjusting performance is very unstable, handles difficulty; When one pump moves simultaneously for a plurality of final controlling element, because of hydraulic oil is to flow to the light final controlling element of load, need carry out throttling to the light actuator control valves bar of load, be engraved in variation during the load of each final controlling element, flow rate distribution reasonably again, very difficult control cooperatively interacts and realizes desired composite move; In the excavator real work of multiple pump, swing arm, dipper, scraper bowl all require and can collaborate, but do not require the interflow sometimes, and realize collaborating sometimes, do not collaborate sometimes is to be difficult to realize.
Summary of the invention:
The purpose of this utility model, provide a kind of load flow pro rate multipath hydraulic control valve, it is after the restriction of the selector valve of multipath hydraulic control valve, a load-sensing chamber is set, in load onto down the pressure compensation spool that moves, lower end, load-sensing chamber is connected with oil input channel by restriction, middle part, load-sensing chamber is connected with the commutation chamber by one-way valve, upper end, load-sensing chamber is connected with the load-sensing oil duct, the pressure signal transmission of final controlling element is given the pressure compensation spool, simultaneously, the load-sensing oil duct of each plate valve is connected, and links to each other with the control mouth of oil hydraulic pump.Each pressure compensation spool is controlled by higher induced pressure all, and the pressure behind each restriction keeps equating that the pressure before each restriction equates that with input pressure the pressure reduction at restriction two ends equates that oil hydraulic pump is pressed the opening slot sectional area direct ratio fuel feeding of restriction.The area of settable orifice changes with spool stroke, and the valve core opening slot cross-section in the stroke end amasss and is directly proportional with each final controlling element demand volume.
The utility model load flow pro rate multipath hydraulic control valve takes following technological scheme to realize, load flow pro rate multi-way valve is the multipath hydraulic control valve of valve block formula oil circuit in parallel, it is by oiling valve, the swing arm selector valve, the scraper bowl selector valve, the dipper selector valve, right lateral is walked selector valve, left lateral is walked selector valve, broken selector valve, the soil-shifting selector valve, second oiling valve, slewing directional control valve and scavenger valve constitute, the multipath hydraulic control valve is connected in the tapped hole of oiling valve by an end of stud bolt, the stud bolt the other end is fastened together by nut, adopts the ring sealing between the surface of contact of each valve block; Second filler opening, second return opening, auxiliary return opening, load-sensing hydraulic fluid port are set on oiling valve.Second filler opening is connected with oil input channel, and second return opening is connected with two back oil roads, and the load-sensing hydraulic fluid port is connected with the load-sensing oil duct.Selector valve is provided with two guide's control ports and two actuator ports; Second oiling valve is provided with first filler opening, and first filler opening is connected with oil input channel; Scavenger valve is provided with first return opening, and first return opening is connected with two back oil roads.Oiling valve is made of safety valve, off-load spool, unloading valve spring, off-load bonnet, relief valve, throttle valve, oil-feed valve body, the unloading valve core apparatus is in the unloading hole of oil-feed valve body, the lower end of unloading hole is connected with oil input channel, the middle part of unloading hole is connected with back oil road, and the top of unloading hole is connected with the load-sensing oil duct.The off-load bonnet is connected with valve body by screw thread, is sealed by ring between off-load bonnet and the valve body.Device unloading valve spring between off-load bonnet and the off-load spool.Safety valve and relief valve and throttle valve are screw-in cartridge valve, are connected on the tapped hole of oil-feed valve body, are sealed by ring between safety valve, relief valve, throttle valve and the oil-feed valve body.Safety valve is connected with second filler opening, the pressure maximum of control system.Relief valve is connected with the load-sensing oil duct, the maximum pressure of control load induction hydraulic fluid port.Throttle valve is connected with the load-sensing oil duct, the flow of control load induction hydraulic fluid port.Selector valve is made of commutation valve body, changeover valve core, two spring seats, two Returnning springs, two cartridge cover, two safety valves, pressure compensation spool, ring, plug screw, screw, two rings, two one-way valves, cartridge cover is by the both sides of screw device at the commutation valve body, seal by ring between cartridge cover and the commutation valve body, the changeover valve core device is in the spool bore of commutation valve body, the variable restrictor groove is set on the changeover valve core, the spring seat device is provided with Returnning spring at the two ends of changeover valve core between spring seat and the cartridge cover.Safety valve is a screw-in cartridge valve, is connected on the tapped hole of commutation valve body, is sealed by ring between safety valve and the commutation valve body.The pressure-compensated valve core apparatus is in the load-sensing chamber of commutation valve body, and the upper end in load-sensing chamber is provided with plug screw, and plug screw is connected on the tapped hole of commutation valve body, is sealed by ring between plug screw and the commutation valve body.The pressure compensation spool moves up and down in the load-sensing chamber, and the middle part in load-sensing chamber is connected with two commutation chambeies by one-way valve, and the upper end in load-sensing chamber is connected with the load-sensing oil duct.
Effect of the present utility model is simple in structure, easy to operate, non-loaded interference phenomenon, the movement velocity of each final controlling element is only relevant with its spool stroke when moving simultaneously, the driver controls its composite move by the hope of oneself, single pump still can keep the independence of each actuator motions for a plurality of final controlling element, when flow is saturated, the speed of each final controlling element is pressed spool stroke equal proportion ground and is descended, still keep original kinematic relation, be widely used in the load flow pro rate multipath hydraulic control valve of mini-excavator Hydraulic Power Transmission System.
Description of drawings:
The utility model load flow pro rate multipath hydraulic control valve will describe in further detail in conjunction with the accompanying drawings.
Fig. 1 is the structural representation of the utility model load flow pro rate multipath hydraulic control valve.
Fig. 2 is the decomposing schematic representation of the utility model load flow pro rate multipath hydraulic control valve valve block.
Fig. 3 is the partial sectional view of load flow pro rate multipath hydraulic control valve oiling valve.
Fig. 4 is the partial sectional view of load flow pro rate multipath hydraulic control valve selector valve.
Fig. 5 is the multipath hydraulic distribution map of the utility model load flow pro rate multipath hydraulic control valve.
Embodiment:
With reference to Fig. 1, the utility model is the multipath hydraulic control valve of valve block formula oil circuit in parallel, it be by oiling valve 1, swing arm selector valve 2, scraper bowl selector valve 3, dipper selector valve 4, right lateral walk selector valve 5, left lateral is walked selector valve 6, broken selector valve 7, soil-shifting selector valve 8, second oiling valve 9, slewing directional control valve 10 and scavenger valve 11 and is constituted, the multipath hydraulic control valve is connected on the tapped hole of oiling valve 1 by stud bolt 13 1 ends, stud bolt 13 the other ends are fastened together by nut 12, and the ring sealing is set between the surface of contact of each valve block.During practical application, can be combined into corresponding multipath hydraulic control valve according to the needs of different machines.
With reference to Fig. 2, second filler opening 19, second return opening 18, auxiliary return opening 21, load-sensing hydraulic fluid port 20 are set on oiling valve 1, second filler opening 19 is connected with oil input channel 24, second return opening 18 and first back oil road 25 are connected with second back oil road 26, and load-sensing hydraulic fluid port 20 is connected with load-sensing oil duct 27.Guide's control port 16 and guide's control port 23 and actuator port 17 and actuator port 22 are set on the swing arm selector valve 2; First filler opening, 15, the first filler openings 15 are set on second oiling valve 9 to be connected with oil input channel 24; First return opening, 14, the first return openings 14 and first back oil road 25 are set on the scavenger valve 11 to be connected with second back oil road 26.
With reference to Fig. 3, the partial sectional view of oiling valve 1, it is by safety valve 34, off-load spool 28, unloading valve spring 29, off-load bonnet 30, relief valve 31, throttle valve 32, oil-feed valve body 33 constitutes, off-load spool 28 devices are in the unloading hole of oil-feed valve body 33, the lower end of unloading hole is connected with oil input channel 24, and the middle part of unloading hole is connected with back oil road 25, and the top of unloading hole is connected with load-sensing oil duct 27; Off-load bonnet 30 is connected with oil-feed valve body 33 by screw thread, is sealed by ring between off-load bonnet 30 and the oil-feed valve body 33; Between off-load bonnet 30 and the off-load spool 28 unloading valve spring 29 is set; Safety valve 34, relief valve 31, throttle valve 32 are screw-in cartridge valve, are connected in the tapped hole of oil-feed valve body 33, are sealed by ring between safety valve 34, relief valve 31, throttle valve 32 and the oil-feed valve body 33; Safety valve 34 is connected with filler opening 15, the pressure maximum of control system; Relief valve 31 is connected with load-sensing oil duct 27, the maximum pressure of control load induction hydraulic fluid port 20; Throttle valve 32 is connected with load-sensing oil duct 27, the flow of control load induction hydraulic fluid port 20.
With reference to Fig. 4, the selector valve partial sectional view, it is to be made of commutation valve body 45, changeover valve core 35, two spring seats 36, two Returnning springs 37, two cartridge cover 38, two safety valves 34, pressure compensation spool 39, ring 40, plug screw 41, a plurality of screw 42, two rings 43, two one-way valves 44; The 24th, oil input channel, 25 is that first back oil road, 26 is second back oil roads, the 46th, the load-sensing chamber, 47 is first commutation chambeies, 48 is second commutation chambeies, the 16th, guide's control port, the 23rd, guide's control port, the 17th, actuator port, the 22nd, actuator port; Cartridge cover 38 is installed in commutation valve body 45 both sides by screw 42, seal by ring 43 between cartridge cover 38 and the commutation valve body 45, changeover valve core 35 devices are in the spool bore of commutation valve body 45, the variable restrictor groove is set on the changeover valve core 35, spring seat 36 devices are provided with Returnning spring 37 at the two ends of changeover valve core 35 between spring seat 36 and the cartridge cover 38; Safety valve 34 is screw-in cartridge valves, is connected in the tapped hole of commutation valve body 45, is sealed by ring between safety valve 34 and the commutation valve body 45; Pressure compensation spool 39 devices are in the load-sensing chamber 46 of commutation valve body 45, and the upper end in load-sensing chamber 46 is provided with plug screw 41, and plug screw 41 is connected in the tapped hole of commutation valve body 45, sealed by ring 40 between plug screw 41 and the commutation valve body 45; Pressure compensation spool 39 moves up and down in the load-sensing chamber, and the middle part in load-sensing chamber is connected with the second commutation chamber 48 by the one-way valve 44 and the first commutation chamber 47, and the upper end in load-sensing chamber is connected with load-sensing oil duct 27.
The embodiment of the utility model load flow pro rate multipath hydraulic control valve, it is in guide's control port of each selector valve during not oil-feed, oil input channel 24 is shut by off-load spool 28 and each changeover valve core, pressure compensation spool 39 is in bottom, actuator port 17 and actuator port 22 sealings, one-way valve 44 is in closed condition, the first commutation chamber 47 and 48 sealings of the second commutation chamber; Input pressure raises compression unloading valve spring 29 and off-load spool 28 is moved up, fluid flows to first back oil road 25 by oil input channel 24 and enters fuel tank, the pressure of load-sensing oil duct 27 is zero, system pressure is the compressive force of unloading valve spring 29 and the pressure sum of load-sensing oil duct 27, and system's meta pressure equals the compressive force of unloading valve spring 29.Left side guide's control port 23 oil-feeds, promoting changeover valve core 35 moves right, move to that throttling groove is connected with oil input channel 24 on the spool 35, fluid begins to enter 46 lower ends, load-sensing chamber, promoting pressure compensation spool 39 moves up, fluid at first enters the middle part in load-sensing chamber 46, open the one-way valve 44 of both sides, fluid enters the commutation chamber, pressure compensation spool 39 continues to move up, fluid is connected with the upper end in load-sensing chamber 46 by the restriction of pressure compensation spool 39 inside, and fluid enters load-sensing oil duct 27, the first commutation chambeies 47 and is connected with actuator port 22, fluid enters actuator port 22, the second commutation chamber 48 still keeps sealing, and actuator port 17 is connected with second back oil road 26, carries out draining.The similar of each selector valve.Guide's control port oil-feed of a selector valve, fluid is successively by the changeover valve core restriction, lower end, load-sensing chamber, the pressure compensator restriction, enter load-sensing oil duct 27, the pressure of load-sensing oil duct 27 equals system's meta pressure at this moment, the compressive force of unloading valve spring 29 just, system pressure is the compressive force of unloading valve spring 29 and the pressure sum of load-sensing oil duct 27, system pressure just is elevated to the pressure of 2 times of unloading valve springs 29, this moment, the pressure of oil input channel 24 remained system's meta pressure, and system pressure is higher than the pressure of oil input channel 24 and makes off-load spool 28 keep closing.Fluid enters middle part, load-sensing chamber, and system pressure is littler than loading demand pressure, and one-way valve keeps closing.The pressure of load-sensing oil duct 27 rises by each compressive force that increases a unloading valve spring 29, system pressure is the compressive force of unloading valve spring 29 and the pressure sum of load-sensing oil duct 27, system pressure continues to rise and reaches the required pressure of load, open one-way valve and enter commutation chamber, actuator port, system pressure no longer rises, and pressure compensator keeps being stabilized in the load-sensing chamber topmost.This is a transients.System pressure comes than the compressive force that the pressure of oil input channel 24 exceeds a unloading valve spring 29, and off-load spool 28 just keeps closing.The pressure difference at changeover valve core restriction two ends equals the compressive force of unloading valve spring 29.Control the position of oil control changeover valve core in the commutation valve body by the guide.The position difference of changeover valve core in the commutation valve body, the flow section size that forms between changeover valve core variable restrictor groove and the valve body is just different, and just different by the flow of changeover valve core restriction, the speed of final controlling element is just different.When load diminishes, the pressure of actuator port diminishes, the pressure of load-sensing oil duct 27 diminishes, system pressure is the compressive force of unloading valve spring 29 and the pressure sum of load-sensing oil duct 27, system pressure diminishes, and oil input channel 24 pressure ratio system pressures are big, and the off-load spool rises, the beginning off-load is reduced to up to oil input channel pressure the off-load spool is closed.System pressure is along with induced pressure diminishes.When load becomes big, it is big that the pressure of actuator port becomes, it is big that the pressure of load-sensing oil duct 27 becomes, the pressure compensation spool is moved down, at first cut off lower end, load-sensing chamber by the oil circuit of pressure compensation valve core inside restriction to load-sensing oil duct 27, the pressure compensation spool continues to move down, the oil circuit that middle part, load-sensing chamber is led in lower end, load-sensing chamber also is cut off, system pressure continues to rise, and system pressure is elevated to the pressure compensation spool is risen again, and oil circuit reopens.System pressure is along with induced pressure becomes big.When induced pressure was too big, the safety valve 34 on the selector valve was opened off-load.When having two or more selector valves to work simultaneously, oil input channel 24 is simultaneously to these several selector valve fuel feeding, because of the load of each final controlling element in different size, therefore the pressure of each actuator port is also different, input pressure at first is elevated to the one-way valve of opening the underload selector valve, enter underloaded final controlling element, but end pressure ambassador pressure compensation spool can not move up on the heavy duty load-sensing chamber, fluid is closed in the lower end in load-sensing chamber.By load-sensing oil duct 27, the highest pressure acts on the upper end of each selector valve pressure compensation spool, the pressure compensation spool of underload selector valve is moved down, the oil-feed of underload selector valve is cut off by the oil circuit of pressure compensation valve core inside restriction to load-sensing oil duct 27, the pressure compensation spool continues to move down, the oil circuit that middle part, load-sensing chamber is led in lower end, load-sensing chamber also is cut off, system pressure continues to rise, system pressure is elevated to pressure compensation spool that heavy load pressure makes light load selector valve connection and rises again and oil circuit is opened, the pressure compensation spool of heavy load selector valve connection also rises simultaneously, and the final controlling element of different pressures demand is started working simultaneously.The pressure reduction at changeover valve core restriction two ends all equals the compressive force of unloading valve spring 29, hydraulic-pressure pump press that changeover valve core throttling groove and selector valve body form flow section direct ratio fuel feeding.During required flow that flow that hydraulic-pressure pump supplies can not satisfy that a plurality of final controlling element work simultaneously, pressure compensation spool in the selector valve all moves down, the pressure reduction at changeover valve core restriction two ends still equates, hydraulic-pressure pump press that changeover valve core throttling groove and selector valve body form flow section direct ratio fuel feeding, only flow is proportional reduces.
Claims (1)
1. load flow pro rate multipath hydraulic control valve, it is by oiling valve (1), swing arm selector valve (2), scraper bowl selector valve (3), dipper selector valve (4), right lateral is walked selector valve (5), left lateral is walked selector valve (6), broken selector valve (7), soil-shifting selector valve (8), second oiling valve (9), slewing directional control valve (10) and scavenger valve (11) constitute, it is characterized in that the multipath hydraulic control valve is connected on the tapped hole of oiling valve (1) by stud bolt (13) one ends, stud bolt (13) the other end is fastened together by nut (12), the multipath hydraulic control valve of valve block formula oil circuit in parallel is provided with the ring sealing between the surface of contact of each valve block; Second filler opening (19) is connected with oil input channel (24), and second return opening (18) and first back oil road (25) are connected with second back oil road (26), and load-sensing hydraulic fluid port (20) is connected with load-sensing oil duct (27); First filler opening (15) is set on second oiling valve (9), and first filler opening (15) is connected with oil input channel (24); First return opening (14) is set on the scavenger valve (11), and first return opening (14) and first back oil road (25) are connected with second back oil road (26); Off-load spool (28) device is in the unloading hole of oil-feed valve body (33), and the lower end of unloading hole is connected with oil input channel (24), and the middle part of unloading hole is connected with first back oil road (25), and the top of unloading hole is connected with load-sensing oil duct (27); Off-load bonnet (30) is connected with oil-feed valve body (33) by screw thread, between off-load bonnet (30) and the off-load spool (28) unloading valve spring (29) is set; Safety valve (34), relief valve (31), throttle valve (32) are screw-in cartridge valve, be connected in the tapped hole of oil-feed valve body (33), cartridge cover (38) is installed in commutation valve body (45) both sides by screw (42), changeover valve core (35) device is in the spool bore of commutation valve body (45), changeover valve core is provided with the variable restrictor groove on (35), spring seat (36) device is provided with Returnning spring (37) at the two ends of changeover valve core (35) between spring seat (36) and the cartridge cover (38); Pressure compensation spool (39) device is in the load-sensing chamber (46) of commutation valve body (45), and the upper end of load-sensing chamber (46) is provided with plug screw (41), and plug screw (41) is connected in the tapped hole of commutation valve body (45); Pressure compensation spool (39) moves up and down in the load-sensing chamber, and the middle part in load-sensing chamber is connected with the second commutation chamber (48) by the one-way valve (44) and the first commutation chamber (47), and the upper end in load-sensing chamber is connected with load-sensing oil duct (27).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009200212512U CN201443544U (en) | 2009-04-16 | 2009-04-16 | Multichannel hydraulic control valve used for prorating load flow |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009200212512U CN201443544U (en) | 2009-04-16 | 2009-04-16 | Multichannel hydraulic control valve used for prorating load flow |
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| CN201443544U true CN201443544U (en) | 2010-04-28 |
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| CN2009200212512U Expired - Fee Related CN201443544U (en) | 2009-04-16 | 2009-04-16 | Multichannel hydraulic control valve used for prorating load flow |
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| CN102242745A (en) * | 2011-07-29 | 2011-11-16 | 竺浩君 | Highly integrated proportion flow distribution valve |
| CN102286989A (en) * | 2011-07-10 | 2011-12-21 | 龙工（上海）挖掘机制造有限公司 | Method for controlling pressure of walking mechanism of excavator |
| CN102312875A (en) * | 2011-08-18 | 2012-01-11 | 长沙中联重工科技发展股份有限公司 | Hydraulic oil flow distribution method and device for hydraulic system |
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| CN102286989B (en) * | 2011-07-10 | 2013-04-03 | 龙工（上海）挖掘机制造有限公司 | Method for controlling pressure of walking mechanism of excavator |
| CN102242745B (en) * | 2011-07-29 | 2014-04-30 | 宁波市博尔法液压有限公司 | Highly integrated proportion flow distribution valve |
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