CN2890448Y - Hydraulic combined control valve - Google Patents
Hydraulic combined control valve Download PDFInfo
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- CN2890448Y CN2890448Y CN 200520052714 CN200520052714U CN2890448Y CN 2890448 Y CN2890448 Y CN 2890448Y CN 200520052714 CN200520052714 CN 200520052714 CN 200520052714 U CN200520052714 U CN 200520052714U CN 2890448 Y CN2890448 Y CN 2890448Y
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Abstract
A hydraulic combined control valve comprises an oil inlet valve plate, a revolving valve plate, a spillover valve plate, an extension valve plate, an amplitude valve plate, a load feedback valve plate, an auxiliary lift valve plate, a main lift valve plate and an oil return valve plate, the valve plates are combined as an integration, a load feedback valve core is positioned in the valve body of load feedback valve plate, the valve bodies of the main and auxiliary lift valve plates is provided with valve rods, a fixed differential reducing valve is arranged in the valve body, a relief pressure valve cartridge is arranged in the fixed differential reducing valve, a spring is positioned between the relief pressure valve cartridge and the valve base. The utility model is used in the hydraulic control system of automobiles, cranes and other vehicles and machinery to manipulate and control the movement of all components, compared with the prior arts, the utility model adopts pilot control mode, when the work pressure of the executive mechanism exceeds the rated value, the pilot overload valve is open, which has the safety protection actions. The stability of the pressure compensation under large flow rate and high pressure can be achieved, and remote control can be conducted, as well as the automation control and continuous proportion control.
Description
Technical field
The utility model belongs to a kind of hydrovalve, particularly a kind of guide proportion control combination control valve with load feedback, pressure compensation that is used for a derrick car hydraulic control system.
Background technique
Hydraulicdirectional control valve is the key element in the machinery hydraulic pressure control systems such as truck crane, high-altitude operation vehicle, excavator, stake machine, special vehicle, is used for handling and controlling the motion of machinery and parts.Its good and bad technical performance that directly influences main computer boxes.Existing selector valve adopts the chip overlaying structure usually, and soon the valve block combine and assemble of multi-disc difference in functionality constitutes the combined operation valve with specific function together, and it handles the manual control of the general employing of control mode.Chinese patent ZL200420030447.5 discloses a kind of " load sensing pressure compensation multi-way valve ".It is made of luffing valve block, flexible valve block, shunting valve block, multichannel valve blocks such as revolution valve block, oil-feed valve block and oil return valve block.Wherein, load sensing valve block and several sensing Reversing valve plates are housed also between luffing valve block and oil return valve block, in the commutation valve body, pressure-compensated valve are housed also.But this valve step-less adjustment working flow changes its movement velocity, and a plurality of executive components are worked under friction speed and different loads pressure synchronously.But this valve adopts the conventional manual mode, can't carry out telecontrol, does not meet modern mechanical product automation control requirement.In addition, can not realize continuous ratio control; On the sensing valve block pressure-compensated valve is set, for the product of high pressure, big flow, for guaranteeing its wall thickness intensity and big latus rectum, gesture is than the size and the difficulty of processing that will increase valve body.Simultaneously, the pressure-compensated valve of this kind structure is under big flow and high pressure, and its pressure compensation stability is not enough; The theoretical drain charge pressure of load-sensing valve drain charge spool design is below the 0.3MPa, but pressure side product moment is bigger before and after it, in actual applications, when system start-up moment, owing to impact excessively, causes that system pressure moment raises, and causes vibration; Whole system pressure is limited by relief valve; corresponding overload protection arrangement is not set according to the different functional requirement of its actuator of engineering goods; easily cause actuator's over pressure work under some functional status, make mechanism components produce distortion, damage, even security incident takes place.
Summary of the invention
The technical problems to be solved in the utility model is to overcome the unfavorable problem of above-mentioned multi-way valve technical performance.Provide a kind of and can realize the control of long-range or automatic ratio, make main frame actuator can require load feedback, the pressure compensation guide proportion control combination control valve of trouble free service down again at different pressure.
The utility model comprises oil-feed valve block, revolution valve block, overflow valve block, flexible valve block, luffing valve block, load feedback valve block, secondary elevator valve block, master winch valve block and oil return valve block, above-mentioned valve block is combined into one, it is characterized in that, oil suction chamber, oil back chamber and load feedback chamber are arranged in the valve body of described load feedback valve block, the load feedback spool is housed in valve body, has on the load feedback spool and oil suction chamber and the corresponding oil inlet hole of oil back chamber and several spill port radially; Active chamber, oil back chamber, pressure feedback chamber and oil suction chamber are arranged in the valve body of described major and minor elevator valve block, valve rod is housed in valve body, have on the valve rod and active chamber, oil back chamber and the corresponding annular groove of oil suction chamber, Fixed differential reducing valve also is housed outside valve body, described Fixed differential reducing valve has a relief pressure valve cartridge, valve seat is equipped with in the outside at relief pressure valve cartridge, between relief pressure valve cartridge and valve seat spring is housed.
One plug-in type precursor overflow valve respectively is housed on load feedback valve block and overflow valve block, described plug-in type precursor overflow valve is by main valve housing, main valve plug, the main valve plug spring, connect valve body, guide's spool, guide's valve seat, pressure regulation spiral shell seat, pressure regulating screw and pressure adjusting spring are formed, the main valve plug spring is installed in the main valve plug, main valve plug is fixed on by bearing pin and connects on the valve body, pressure regulation spiral shell seat is installed in the other end that connects valve body, guide's valve seat is installed in the connection valve body of this end, pressure regulating screw is installed on the pressure regulation spiral shell seat, guide's spool and guide's valve seat offset, and spring is between guide's spool and pressure regulating screw.
Leading, same end on secondary elevator valve block and the luffing valve block respectively is equipped with a plug-in type overload valve, described overload valve is by core bar, main valve plug, valve seat, spring, the poppet valve seat, bell tap, the poppet valve pin, the poppet valve cover, pressure adjusting spring, spring seat and look nut are formed, core bar one end inserts in the main valve plug hole, one end inserts in the poppet valve seat hole, spring is positioned at core bar and poppet valve seat two ends, main valve plug and poppet valve seat are together packed in the valve seat, poppet valve pin and spring seat are packed in the poppet valve trepanning, pressure adjusting spring is positioned at poppet valve pin and spring seat two ends, look nut is loaded on poppet valve cover outer end, offset with spring seat, valve seat and the poppet valve cover bell tap of packing into that offsets, poppet valve pin and core bar offset.
On secondary elevator valve block, shuttle valve is housed, the oil inlet hole of shuttle valve both sides is connected with pressure signal selecting hole on the major and minor elevator valve body respectively, load feedback chamber in pressure signal hole and the load feedback valve body is connected, and the oil inlet hole of shuttle valve both sides is connected with outer control mouth on the major and minor elevator valve body.
Three radial direction oil hole are arranged on the valve rod of major and minor elevator valve block, and three radial direction oil hole are connected by axial bore.
On the valve rod of major-minor elevator, luffing, flexible, revolution valve block, the hydraulic control Effector is housed, described valve rod hydraulic control Effector is made up of a positioning screwn, two spring seats, an inner spring, an outer spring and two seal closures, a spring seat is stuck in valve rod positioning screwn upper end, a spring seat is stuck in the valve rod upper end, inside and outside spring is between two spring seats, and be in the seal closure of valve block upper end, another seal closure is loaded on the valve rod lower end.
Advantage of the present utility model is:
1, the same end of the utility model on major and minor elevator valve block and luffing valve block respectively is equipped with a plug-in type overload valve; adopt guide's control mode, make actuator under different functional statuses, when the working pressure overrate; guide's overload valve is opened thereupon, plays the safety protection effect.
2, at major and minor elevator valve block the external Fixed differential reducing valve is set respectively, and keeps constant principle, be implemented under big flow and the high pressure pressure compensated stability by the upper and lower cavity pressure difference of relief pressure valve cartridge.
3, on the valve rod of major-minor elevator, luffing, flexible, revolution valve block, the hydraulic control Effector is set, utilizes the hydraulic oil of setting pressure, can carry out telecontrol, realize that automation control and continuous ratio control.
Description of drawings
Fig. 1 is a structural representation of the present utility model;
Fig. 2 is the A-A sectional view of Fig. 1;
Fig. 3 is the B-B sectional view of Fig. 1;
Fig. 4 is a fundamental diagram of the present utility model;
Fig. 5 is that the utility model is manually controlled secondary elevator valve block sectional view;
Fig. 6 is the utility model adds normal opening one-way spool in the drain charge spool a load feedback valve block sectional view.
Embodiment
Below in conjunction with accompanying drawing, details are as follows to embodiment:
In Fig. 1: the utility model comprises oil return valve block 1, master winch valve block 2, secondary elevator valve block 3, load feedback valve block 4, luffing valve block 5, flexible valve block 6, overflow valve block 7, revolution valve block 8 and oil-feed valve block 9, hydraulic fluid port T2 and pressure tap G3 are arranged on oil return valve block 1, hydraulic fluid port A5 is arranged on master winch valve block 2, hydraulic fluid port B5, hydraulic control mouth X5, hydraulic control mouth Y5 and outside control mouth W2, on secondary elevator valve block 3, hydraulic fluid port A4 is arranged, hydraulic fluid port B4, hydraulic control mouth X4, hydraulic control mouth Y4 and outside control mouth W1, hydraulic fluid port P3 is arranged on load feedback valve block 4, telecontrol mouth V2, hydraulic fluid port A3 is arranged on luffing valve block 5, hydraulic fluid port B3, hydraulic control mouth X3, hydraulic control mouth Y3, on flexible valve block 6, hydraulic fluid port A2 is arranged, hydraulic fluid port B2, hydraulic control mouth X2, hydraulic control mouth Y2, hydraulic fluid port P2 is arranged on overflow valve block 7, hydraulic fluid port T1, pressure tap G2 and telecontrol mouth V1, on revolution valve block 8, hydraulic fluid port A1 is arranged, hydraulic fluid port B1, hydraulic control mouth X1 and hydraulic control mouth Y1 have hydraulic fluid port P1 and pressure tap G1 on oil-feed valve block 9.
In Fig. 2: secondary elevator valve block 3 has a valve body 30, and hydraulic fluid port A4, hydraulic fluid port B4 and outside control mouth W1 are arranged on the valve body 30, and active chamber a2, active chamber a3, oil back chamber a1, oil back chamber a8, pressure feedback chamber a7, oil suction chamber a10 and adapter cavity a11 are arranged in the valve body 30; On valve body 30, also have two pressure signal selecting hole a4 and a6, pressure signal hole a5, a pressure feedback hole a9; Valve rod 31 is housed in valve body 30, has on the valve rod 31 and the corresponding annular groove b5 of active chamber a2, active chamber a3, b6; Three radial hole b1, b2, b4 are arranged on the valve rod 31 of secondary elevator valve block 3, and three radial holes are connected by axial bore b3; Overload valve also is housed on valve body 30, overload valve is between oil pocket a2 and oil pocket a1, described overload valve is the thread cartridge formula, core bar 29 1 ends insert in the hole of main valve plug 27, one end inserts in the hole of poppet valve seat 24, spring 26 is positioned at the two ends of core bar 29 and poppet valve seat 24, main valve plug 27 is together packed into poppet valve seat 24 in the valve seat 28, poppet valve pin 22 and spring seat 20 poppet valve of packing into overlaps in 23 holes, pressure adjusting spring 21 is positioned at poppet valve pin 22 and spring seat 20 two ends, look nut 19 is loaded on poppet valve and overlaps 23 outer ends, offsets with spring seat 20, and valve seat 28 and poppet valve cover 23 offset and pack in the bell tap 25, poppet valve pin 22 offsets with core bar 29, be connected on the valve body 30 by bell tap 25, when active chamber B4 pressure overrate, poppet valve pin 22 is at first opened, by main valve plug 27 overflows, play overload protective function again; On valve body 30, shuttle valve is housed, described shuttle valve is by steel ball 32, stifled 33 form, steel ball 32 and stifled 33 is installed on the valve body 30, stifled 33 center hole is connected with pressure feedback chamber a7 and the hydraulic fluid port W1 on the valve body 30, oilhole a4 is communicated with the pressure feedback chamber of master winch valve block 2, described steel ball 32 move left and right under the effect of its both sides oil pressure, the side closure that oil pressure is lower, the oil inlet hole a4 of shuttle valve both sides and oil inlet hole a6 are connected with pressure signal hole a5 on the valve body 30 respectively, and pressure signal hole a5 is connected with load feedback chamber f1 on the load feedback valve block 4; At the left Side of secondary elevator valve block 3 Fixed differential reducing valve is installed, described Fixed differential reducing valve has a valve body 10, be equipped with stifled 13 at the two ends of relief pressure valve cartridge 11, between relief pressure valve cartridge 11 upper ends and stifled 13, spring 12 is housed, oilhole d1, d2 are arranged on relief pressure valve cartridge 11, the lower end oil pocket c1 of relief pressure valve cartridge 11 is connected with oil suction chamber a10 by oilhole d1, and the upper end oil pocket c3 of relief pressure valve cartridge 11 is connected with oil pocket c2 by oilhole d2, and oil pocket c2 is connected with pressure feedback chamber a7 by oilhole a9; The hydraulic control Effector is equipped with at valve rod 31 two ends at secondary elevator valve block 3.In the time of according to actual needs, can use manually control, see Fig. 5 at the upper end of valve rod 31 configuration spring reverse motion; Described hydraulic control Effector is made up of cover 14, spring seat 15, positioning screwn 18, outer spring 16, inner spring 17 and end cap 34, a spring seat 15 is stuck in the upper end of positioning screwn 18, another spring seat 15 is stuck in the top of valve rod 31, outer spring 16 and inner spring 17 are between two spring seats 15, valve rod 31 is remained on the neutral position of valve body 30, between spring seat 15 and cover, oil pocket e2 is arranged, oil pocket e1 is arranged between spring seat 15 and end cap, and the control oil by oilhole Y4 and oilhole X4 enters oil pocket e2 and oil pocket e1 promotes valve rod 31 commutations.
In Fig. 3: load feedback valve block 4 has a valve body 37, oil suction chamber f3, oil back chamber f2, oil back chamber f4 and load feedback chamber f1 are arranged in the valve body 37, also have an oil inlet P 3 on valve body 37, oil inlet P 3 is connected with oil suction chamber f3, and oil suction chamber f3 is connected with hydraulic fluid port P2; Load feedback spool 38 is housed in valve body 37, there is an endoporus g1 lower end of load feedback spool 38, be connected with the radial hole not of uniform size of some on the spool 38, in spool 38 upper ends one damper rod 42 is arranged, in the upper end of load feedback spool 38 lid 42 is installed, spring seat 41 is housed in lid 42, outer spring 40 and inner spring 39 are between load feedback spool 38 and spring seat 41, load feedback chamber f1 is arranged in the upper end of load feedback spool 38, and oil pocket f1 communicates with pressure signal hole a5.According to existing actual conditions, the instantaneous pressure superelevation phenomenon when reducing system start-up can be provided with a drain charge spool 57 in the load feedback valve block, add a normal opening one-way spool 58 in drain charge spool 57, plays shunting and damping effect, sees Fig. 6; The other end at valve body 37 is equipped with a plug-in type relief valve, described relief valve is by by main valve housing 44, main valve plug 46, main valve plug spring 45, bearing pin 48, connect valve body 52, guide's spool 50, guide's valve seat 49, pressure regulation spiral shell seat 53, pressure regulating screw 55, pressure adjusting spring 51 and locking nut 54 are formed, have and oil pocket f3, the corresponding oilhole h5 of oil pocket f4, oil pocket h4, oilhole h3, oil pocket h1 and oilhole h2, main valve plug spring 45 is installed in the main valve plug 46, main valve plug 46 is fixed on by bearing pin 48 and connects on the valve body 52, pressure regulation spiral shell seat 53 is installed in the other end that connects valve body 52,49 interference of guide's valve seat are pressed into and connect in the valve body 52, pressure regulating screw 55 is installed on the pressure regulation spiral shell seat 53, guide's spool 50 and guide's valve seat 49 offset, pressure adjusting spring 51 is between guide's spool 50 and pressure regulating screw 55, on the external diameter circumference that connects valve body 52 four uniform radial direction oil hole are arranged, wherein any can be used as V2 telecontrol hydraulic fluid port.
Work control procedure of the present utility model is as shown in Figure 4:
Hydraulic fluid port P1 oil-feed, for the work of revolution valve block 8, when pressure oil when hydraulic fluid port P1 enters into hydraulic fluid port A1, hydraulic fluid port B1 oil return; When pressure oil when hydraulic fluid port P1 enters into hydraulic fluid port B1, hydraulic fluid port A1 oil return.
Hydraulic fluid port P2 oil-feed for luffing valve block 5,6 work of flexible valve block, with the pressure oil interflow that enters through hydraulic fluid port P3, realizes the associating of major and minor elevator or load feedback control separately simultaneously.
When the valve rod 31 on major and minor elevator valve block 2 and 3 is positioned at the neutral position, the pressure oil that enters through hydraulic fluid port P2 and hydraulic fluid port P3 collaborates in valve, enter load feedback valve block 4, enter in the load feedback spool 38 through oil suction chamber f3, oil inlet hole g1, promote load feedback spool 38 and move up, through oilhole g2 drain charge.
When major and minor elevator valve block 2 or 3 commutations, active chamber a2 or active chamber a3 communicate with pressure feedback chamber a7, at this moment, pressure oil enters load feedback chamber f1 by pressure signal hole a5, load feedback chamber f1 equates with oil suction chamber f3 pressure, by load feedback spool 38 both ends of the surface product moments, load feedback spool 38 is closed.At this moment, active chamber a2 or active chamber a3 communicate with pressure feedback chamber a7, pressure oil is input pressure through the lower end that pressure signal hole a5 enters load feedback chamber f1, load feedback spool 38, the upper end is an induced pressure, pressure reduction between input pressure and the induced pressure is 0.7～1.0MPa, and the servo-actuated variation along with load variations, realize load feedback control; In valve rod 31 valve port opening one regularly, it not with load variations, realizes constant flux control by the constant flow of pressure oil, guarantees the flow rigidity of control system.
Hydraulic fluid port A5 on major and minor elevator valve block 2 and 3, hydraulic fluid port B5, hydraulic fluid port A4, when hydraulic fluid port B4 works simultaneously, because pressure feedback chamber a7 and load feedback chamber f1 normal open, the pressure difference of input pressure and pressure feedback chamber a7 equals constant, because pressure feedback chamber a7, load feedback chamber f1 are connected all the time with pressure signal hole a5, so be not subjected to the pressure influence of low active chamber a2 or active chamber a3, realize the requirement of a plurality of equipment synchronous workings under the different loads.
The utility model is a kind of hydraulic pressure combination control valve that more is applicable to the open loop hydraulic control system that existing metering pump is formed.
Claims (8)
1, hydraulic pressure combination control valve, comprise oil-feed valve block, revolution valve block, overflow valve block, flexible valve block, luffing valve block, load feedback valve block, secondary elevator valve block, master winch valve block and oil return valve block, it is characterized in that, oil suction chamber, oil back chamber and load feedback chamber are arranged in the valve body of described load feedback valve block, the load feedback spool is housed in valve body, has on the load feedback spool and oil suction chamber and the corresponding oil inlet hole of oil back chamber and several spill port radially; Active chamber, oil back chamber, pressure feedback chamber and oil suction chamber are arranged in the valve body of described major and minor elevator valve block, valve rod is housed in valve body, have on the valve rod and active chamber, oil back chamber and the corresponding annular groove of oil suction chamber, Fixed differential reducing valve also is housed outside valve body, described Fixed differential reducing valve has a relief pressure valve cartridge, valve seat is equipped with in the outside at relief pressure valve cartridge, between relief pressure valve cartridge and valve seat spring is housed.
2, hydraulic pressure combination control valve according to claim 1, it is characterized in that, one plug-in type precursor overflow valve respectively is housed on load feedback valve block and overflow valve block, described plug-in type precursor overflow valve is by main valve housing, main valve plug, the main valve plug spring, connect valve body, guide's spool, guide's valve seat, pressure regulation spiral shell seat, pressure regulating screw and pressure adjusting spring are formed, the main valve plug spring is installed in the main valve plug, main valve plug is fixed on by bearing pin and connects on the valve body, pressuring adjusting valve base is installed in the other end that connects valve body, guide's valve seat is installed in the connection valve body of this end, pressure regulating screw is installed on the pressure regulation spiral shell seat, guide's spool and guide's valve seat offset, and spring is between guide's spool and pressure regulating screw.
3; hydraulic pressure combination control valve according to claim 1; it is characterized in that; leading; same end on secondary elevator valve block and the luffing valve block respectively is equipped with a plug-in type overload protection valve; described overload protection valve is by core bar; main valve plug; valve seat; spring; the poppet valve seat; bell tap; the poppet valve pin; the poppet valve cover; pressure adjusting spring; spring seat and look nut are formed; core bar one end inserts in the main valve plug hole; one end inserts in the poppet valve seat hole; spring is positioned at core bar and poppet valve seat two ends; main valve plug and poppet valve seat are together packed in the valve seat; poppet valve pin and spring seat are packed in the poppet valve trepanning; pressure adjusting spring is positioned at poppet valve pin and spring seat two ends; look nut is loaded on poppet valve cover outer end; offset with spring seat; valve seat and the poppet valve cover bell tap of packing into that offsets, poppet valve pin and core bar offset.
4, hydraulic pressure combination control valve according to claim 1, it is characterized in that, on secondary elevator valve block, shuttle valve is housed, the oil inlet hole of shuttle valve both sides is connected with pressure signal selecting hole on the major and minor elevator valve body respectively, load feedback chamber in pressure signal hole and the load feedback valve body is connected, and the oil inlet hole of shuttle valve both sides also is connected with outer control mouth on the major and minor elevator valve body.
5, hydraulic pressure combination control valve according to claim 1 is characterized in that three radial direction oil hole are arranged on the valve rod of major and minor elevator valve block, and three radial direction oil hole are connected by axial bore.
6, hydraulic pressure combination control valve according to claim 1, it is characterized in that, on the valve rod of major-minor elevator, luffing, flexible, revolution valve block, the hydraulic control Effector is housed, described valve rod hydraulic control Effector is made up of a positioning screwn, two spring seats, an inner spring, an outer spring and two seal closures, a spring seat is stuck in valve rod positioning screwn upper end, a spring seat is stuck in the valve rod upper end, inside and outside spring is between two spring seats, and be in the seal closure of valve block upper end, another seal closure is loaded on the valve rod lower end.
7, hydraulic pressure combination control valve according to claim 1 is characterized in that, is provided with normal opening one-way spool in the drain charge spool of load feedback valve block.
8, hydraulic pressure combination control valve according to claim 6 is characterized in that, in major-minor elevator, luffing, valve rod upper end flexible, the revolution valve block spring reverse motion is housed.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200520052714 CN2890448Y (en) | 2005-12-08 | 2005-12-08 | Hydraulic combined control valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200520052714 CN2890448Y (en) | 2005-12-08 | 2005-12-08 | Hydraulic combined control valve |
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| CN2890448Y true CN2890448Y (en) | 2007-04-18 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN 200520052714 Expired - Lifetime CN2890448Y (en) | 2005-12-08 | 2005-12-08 | Hydraulic combined control valve |
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Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101929481A (en) * | 2010-04-30 | 2010-12-29 | 北京联合大学 | Three-way pressure compensating valve for hydraulic energy-saving system |
| CN102330714A (en) * | 2011-10-18 | 2012-01-25 | 常德中联重科液压有限公司 | Load feedback control valve |
| CN101550957B (en) * | 2008-03-31 | 2013-04-03 | 中国航空工业第一集团公司北京航空精密机械研究所 | Separate electro-hydraulic servo valve |
| CN103148039A (en) * | 2013-03-20 | 2013-06-12 | 锦州市力特缸泵阀液压制造有限公司 | Dual-pump two-way converging multi-tandem direction valve |
| CN103899588A (en) * | 2014-01-17 | 2014-07-02 | 徐州徐工随车起重机有限公司 | Lorry-mounted crane multi-way reversing device and straight arm lorry-mounted crane |
| CN104358728A (en) * | 2014-11-04 | 2015-02-18 | 浙江大学 | Secondary load control valve integrating overflow function on pilot valve core |
| CN104653820A (en) * | 2015-03-17 | 2015-05-27 | 泸州精通流体液压机械有限公司 | Multi-way valve for small-sized excavator |
| CN104912868A (en) * | 2015-07-06 | 2015-09-16 | 玉林市富山液压件制造有限公司 | Combined oil source valve |
| CN106151146A (en) * | 2016-08-29 | 2016-11-23 | 丰隆高科液压股份有限公司 | A kind of from decompression stress sensing multiple directional control valve and operation principle thereof |
| CN108223479A (en) * | 2018-01-31 | 2018-06-29 | 邹城市益凯德液压有限公司 | The high flow manual reversal valve of included overload protection |
| CN113544390A (en) * | 2019-09-25 | 2021-10-22 | 日立建机株式会社 | Flow control valve |
| CN114458645A (en) * | 2021-12-31 | 2022-05-10 | 湖南中联重科智能高空作业机械有限公司 | Hydraulic system for aerial work machine and aerial work machine |
| CN116164002A (en) * | 2022-12-30 | 2023-05-26 | 广东智能无人系统研究院(南沙) | Integrated load sensing proportional valve with light combined valve core |
-
2005
- 2005-12-08 CN CN 200520052714 patent/CN2890448Y/en not_active Expired - Lifetime
Cited By (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101550957B (en) * | 2008-03-31 | 2013-04-03 | 中国航空工业第一集团公司北京航空精密机械研究所 | Separate electro-hydraulic servo valve |
| CN101929481A (en) * | 2010-04-30 | 2010-12-29 | 北京联合大学 | Three-way pressure compensating valve for hydraulic energy-saving system |
| CN102330714A (en) * | 2011-10-18 | 2012-01-25 | 常德中联重科液压有限公司 | Load feedback control valve |
| CN103148039B (en) * | 2013-03-20 | 2015-09-23 | 锦州市力特缸泵阀液压制造有限公司 | Double pump two-way interflow multiple directional control valve |
| CN103148039A (en) * | 2013-03-20 | 2013-06-12 | 锦州市力特缸泵阀液压制造有限公司 | Dual-pump two-way converging multi-tandem direction valve |
| CN103899588A (en) * | 2014-01-17 | 2014-07-02 | 徐州徐工随车起重机有限公司 | Lorry-mounted crane multi-way reversing device and straight arm lorry-mounted crane |
| CN104358728A (en) * | 2014-11-04 | 2015-02-18 | 浙江大学 | Secondary load control valve integrating overflow function on pilot valve core |
| CN104653820A (en) * | 2015-03-17 | 2015-05-27 | 泸州精通流体液压机械有限公司 | Multi-way valve for small-sized excavator |
| CN104912868A (en) * | 2015-07-06 | 2015-09-16 | 玉林市富山液压件制造有限公司 | Combined oil source valve |
| CN106151146A (en) * | 2016-08-29 | 2016-11-23 | 丰隆高科液压股份有限公司 | A kind of from decompression stress sensing multiple directional control valve and operation principle thereof |
| CN108223479A (en) * | 2018-01-31 | 2018-06-29 | 邹城市益凯德液压有限公司 | The high flow manual reversal valve of included overload protection |
| CN108223479B (en) * | 2018-01-31 | 2024-03-29 | 山东益凯德液压股份有限公司 | Large-flow manual reversing valve with overload protection |
| CN113544390A (en) * | 2019-09-25 | 2021-10-22 | 日立建机株式会社 | Flow control valve |
| CN113544390B (en) * | 2019-09-25 | 2024-06-11 | 日立建机株式会社 | Flow control valve |
| CN114458645A (en) * | 2021-12-31 | 2022-05-10 | 湖南中联重科智能高空作业机械有限公司 | Hydraulic system for aerial work machine and aerial work machine |
| CN114458645B (en) * | 2021-12-31 | 2024-02-20 | 湖南中联重科智能高空作业机械有限公司 | Hydraulic system for an overhead working machine and overhead working machine |
| CN116164002A (en) * | 2022-12-30 | 2023-05-26 | 广东智能无人系统研究院(南沙) | Integrated load sensing proportional valve with light combined valve core |
| CN116164002B (en) * | 2022-12-30 | 2023-08-08 | 广东智能无人系统研究院(南沙) | Integrated load sensing proportional valve with light combined valve core |
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| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C56 | Change in the name or address of the patentee |
Owner name: CHANGDE ZHONGLIAN ZHONGKE HYDRAULIC CO., LTD. Free format text: FORMER NAME: CHANGDE XINCHENG HYDRAULIC CO., LTD. |
|
| CP01 | Change in the name or title of a patent holder |
Address after: 415000, Changde, Hunan Province, Wuling District, Ji Ting Road, No. 2 Patentee after: Changde Zhonglian Zhongke Hydraulic Co., Ltd. Address before: 415000, Changde, Hunan Province, Wuling District, Ji Ting Road, No. 2 Patentee before: Xincheng Hydraulic Co., Ltd., Changde |
|
| CX01 | Expiry of patent term |
Granted publication date: 20070418 |
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| EXPY | Termination of patent right or utility model |