CN201610873U - Multifunctional highly-integrated multi-way valve - Google Patents
Multifunctional highly-integrated multi-way valve Download PDFInfo
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- CN201610873U CN201610873U CN2010292110212U CN201029211021U CN201610873U CN 201610873 U CN201610873 U CN 201610873U CN 2010292110212 U CN2010292110212 U CN 2010292110212U CN 201029211021 U CN201029211021 U CN 201029211021U CN 201610873 U CN201610873 U CN 201610873U
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Abstract
The utility model relates to a multifunctional highly-integrated multi-way valve, wherein an inlet valve block and an oil return valve block or a gap bridge valve block are arranged at two ends respectively, one or more of a balance valve directional valve block, a Q type function directional valve block, a pilot type hydraulic lock directional valve block, a backflushing reset directional valve block, a speed-regulating directional valve block, an overload interflow valve block, a hydraulic control directional valve block, a pneumatic control reversing valve block and an overload and oil supplement reversing valve block are arranged in the middle, the valve body of each valve block is provided with four public connecting holes correspondingly, through which four double end screws penetrates, then the four double end screws are screwed with the nuts, so that the valve blocks are integrated, the valve blocks are communicated with each other by parallel channels, middle channels and low pressure channels at the side surfaces to form a complete hydraulic control oil-way. The multifunctional highly-integrated multi-way valve is integrated with the reversing function by a threaded mode and has the advantages of delicate structure, high use pressure, less flow channel pressure, adequate oil flow, flexible configuration and beautiful appearance.
Description
Technical field
The utility model belongs to the hydraulic control device technical field, is specifically related to a kind of multi-functional integrated form multiple directional control valve that has.
Background technique
The employed oil circuit control mode of existing multiple directional control valve is;
(1) because diversity, the complexity of engineering machinery and other all kinds of hydraulic machinery functions of use, cause hydraulic element manufacturer for adapting to its needs, have no alternative but satisfy its specific (special) requirements for its all kinds of special functions development kinds reach tens of kinds special-purpose multiple directional control valve, cause model mixed and disorderly, the configuration feature imperfection, match selection is limited.Hydraulic parts manufacturer then because the specification kind is too much, is caused the development cost height, and the lead time is long, lots of production is little, cost up, and competitive ability descends.
(2) adopt existing multiple directional control valve to increase the requirement that different control valves is realized its control oil channel in addition in hydraulic system, it is complicated to cause pipeline to connect, and volume is big, inconvenience is installed, and the reaction susceptibility reduces, and the external leakage possibility increases, cost up, system reliability reduces.
(3) ZL (or DL) working pressure that designed before 30 years of existing combined type multiple directional control valve can reach the 31.5Mpa, and other working pressure is all below 25Mpa.And ZL (or DL) multiple directional control valve volume is big, the high pressure sealing difficulty, leakage rate causes power loss big greatly between sheet, the reversing maneuver difficulty, have no alternative but adopt and reduce working pressure, increase the ability present situation that oil cylinder cylinder diameter or oil hydraulic motor discharge capacity adapt to multiple directional control valve.
In view of the foregoing, press for for engineering machinery and other all kinds of hydraulic machineries develop a kind of widely applicable, the novel high integrated multifunction multi-way valve that performance significantly improves.
The model utility content
The problems referred to above that the utility model exists at prior art, a kind of high integrated multifunction multi-way valve is proposed, diverter valve, interflow valve, the control valve functions improvement structural designs such as valve, overload valve, Fill valve that reset that recoil with existing topical application are integrated in respectively in this multiple directional control valve group; Simultaneously, still the function brand-new design such as equilibrium valve, series flow control valve, leading type hydraulic lock of not having applied in any combination is integrated in this multiple directional control valve group, adopt valve body profile, public oil inlet hole, public spill port, the on all four valve body structure of public attachment hole equidimension, by different integration modes, it is perfect relatively to constitute function, working pressure 31.5Mpa, range of flow 15mm latus rectum, 100L/min; The 22mm latus rectum, 180L/min; The 28mm latus rectum, 280L/min, elegant in shape, good manufacturability, applied widely, the Multifunction multiple directional control valve that level of integration is high.Can realize effective control by different control oil channel is formed in the set of various selector valve groups to all kinds of hydraulic machineries.
The utility model is specifically realized by the following technical solutions:
The two ends of the high integrated multifunction multi-way valve that the utility model proposes are arranged oiling valve group and scavenger valve group or gap bridge valve group respectively, intermediate arrangement equilibrium valve selector valve group, Q type function selector valve group, leading type hydraulic lock selector valve group, recoil reset the arbitrary valve group among selector valve group, timing reversal valve group, overload interflow valve group, pilot operated directional control valve group, air-actuated direction valve group and overload, the repairing selector valve group or the combination of a plurality of valve groups; On the valve body of above-mentioned each valve group mutually correspondence be provided with four public attachment holes, adopt four double threaded screws to pass, connect as one by nut tension; Be interconnected by the parallel port of side, middle bit port and low-pressure channel between each valve group, form complete hydraulic control oil circuit.
Wherein the oiling valve group can be with the oiling valve group of pressure controlled oiling valve group or band flow-dividing control, can only select a kind ofly during combination as required, and scavenger valve group and gap bridge valve group also can only be selected a kind of as required.
Various control valve of the present utility model all adopts the thread cartridge mode, organically blend with commutation function and become one, advantage such as have delicate structure, working pressure height, the flowpath pressure loss is little, oil filling capacity is big, flexible configuration is various, feedback is sensitive, manipulation is light, beautiful shape, maintenance are convenient; Can realize the multiple pressure control of hydraulic system and hydraulic actuator and conversion, adjusting, locking, the branch of movement velocity are collaborated functions such as selection, pressure control, system protection; and have series parallel connection oil circuit pattern and manually, hydraulic control, gas control, recoil reset etc. and to handle control mode; versatility is good, applied range, can be widely used in various engineering machinery, railway machinery, highway machinery, building machinery, mining machinery, energy machinery, environmental sanitation machinery, farm machinery, ship machinery, army's construction machinery etc.
The utility model specifically has the following advantages:
1, the multiple directional control valve of having filled up present production does not have the blank of integrated equilibrium valve, unidirectional series flow control valve, leading type hydraulic lock function;
2, defectives such as to add inconvenience and volume that equilibrium valve, unidirectional series flow control valve, hydraulic lock bring big, and the pipeline connection reliability is poor, and feedback sensitivity lags behind, and installation conditions is limited have been changed;
3, commutation valve body of the present utility model is guaranteeing under the long-pending enough situations of logical pasta, adopted high low pressure runner parting seal in the valve body side, reduce zone of high pressure, valve body side lifting surface area as far as possible, eliminated between the valve body sheet and leaked, valve opening compressive deformation amount is little, hydraulic card clamping force reduces, and guiding valve reversing maneuver power significantly reduces.It is big at 25～31.5Mpa zone of high pressure valve body amount of deformation to have changed original multiple directional control valve, and leakage rate is big between sheet, raises to press difficulty, the defective that steering force is big.
4, owing to the level of integration height, diverse in function, flexible configuration, pressure and flow coverage area are big, have good versatility, and it is mixed and disorderly to change original combined type multiple directional control valve kind largely, the simple present situation of function.
Description of drawings
Figure 1 shows that the utility model integrated form multi-way valve combination shape assumption diagram
Fig. 2 is that the K of Fig. 1 is to view
Fig. 3 is the D-D sectional view of Fig. 1
Fig. 4 is the hydraulic schematic diagram of Fig. 1
Among the figure: (1) shunting oiling valve group; (2) equilibrium valve selector valve group; (3) Q type function selector valve group; (4) leading type hydraulic lock selector valve group; (5) the recoil selector valve group that resets; (6) timing reversal valve group; (7) overload interflow valve group; (8) pilot operated directional control valve group; (9) air-actuated direction valve group; (10) overload, repairing selector valve group; (11) gap bridge valve; (12) double threaded screw; (13) nut; (14) parallel port; (15) bit port in; (16) low-pressure channel
Embodiment
Further specify structure of the present utility model below in conjunction with accompanying drawing:
Referring to Fig. 1, Fig. 2 and Fig. 3, the high integrated multifunction multi-way valve that this example shows is made up of reset selector valve group 5, timing reversal valve group 6, overload interflow valve group 7, pilot operated directional control valve group 8, air-actuated direction valve group 9, overload, repairing selector valve group 10 and gap bridge valve group 11 of shunting oiling valve group 1, equilibrium valve selector valve group 2, Q type function selector valve group 3, leading type hydraulic lock selector valve group 4, recoil.
Wherein oiling valve group 1 and gap bridge valve group 11 are arranged in the two ends of high integrated multifunction multi-way valve, between them, arrange equilibrium valve selector valve group 2 from right to left successively, Q type function selector valve group 3, leading type hydraulic lock selector valve group 4, the selector valve group 5 that resets recoils, timing reversal valve group 6, overload interflow valve group 7, pilot operated directional control valve group 8, air-actuated direction valve group 9 and overload, repairing selector valve group 10, more than on the valve body of each valve group mutually correspondence be provided with four public attachment holes, adopt four double threaded screws 12 to pass, double threaded screw 12 two ends connect as one by nut 13 tensions.Parallel port 14, middle bit port 15 and low-pressure channel 16 by the side between each valve group are interconnected, and form complete hydraulic control oil circuit.
Oiling valve group 1 can adopt the oiling valve group with pressure controlled oiling valve group or band flow-dividing control, and the scavenger valve group can adopt pressure oil output for the gap bridge valve group of other oil circuit use or the scavenger valve group of straight-through back oil road.This high integrated multifunction multi-way valve is by inside nominal diameter: 15mm, 22mm, 28mm, and nominal flow rate is respectively: 100L/min, 180L/min, 280L/min, nominal pressure: 31.5MPa.
The hydraulic principle of this high integrated multifunction multi-way valve is referring to Fig. 4:
When being illustrated as this example and being in the neutral position, the first pressure oil P1 enters through diverter valve oiling valve group 1, the one tunnel through stable shunting after hydraulic fluid port Z outwards exports, delivery pressure is controlled by safety valve; Equilibrium valve selector valve group 2, Q type function selector valve group 3, leading type hydraulic lock selector valve group 4, the recoil that the residual flow of another road after shunting enters the parallel connection type oil circuit through sequence control valve the reset parallel port 14 and the middle bit port 15 of selector valve group 5, timing reversal valve group 6 are communicated with the pilot pressure of overload valve 1 with regulating system simultaneously.The second pressure oil P2 through overload interflow valve group 7 enter in the valve group, with the parallel port 14 of pilot operated directional control valve group 8 with neutral passage 15 communicates and enter pilot operated directional control valve group 8, air-actuated direction valve group 9 and the overload of serial type oil circuit, the parallel port 14 and the middle bit ports 15 of repairing selector valve group 10 with neutral passage 15 oil of preceding end valve group, the pressure behind the interflow is controlled by overload valve 2 simultaneously.When being illustrated as all selector valve groups and all being in the neutral position, the first pressure oil P1 after shunting residual flow and the second pressure oil P2 by the neutral passage 15 that communicates with all selector valve groups through the hydraulic fluid port Pj of gap bridge valve group 11 output.
The working principle of each selector valve group wherein:
1, when manipulation equilibrium valve selector valve group 2 commutated left, the off-load oil circuit of neutral passage 15 was cut off, and the one-way valve oil circuit that the first pressure oil P1 opens the equilibrium valve 1 that is built in the valve body enters executive component one end active chamber through hydraulic fluid port A1.After low-pressure channel 16 returns fuel tank through hydraulic fluid port T, the variation of return pressure will be regulated the speed of oil return speed in the control requirement of satisfying 2 pairs of cracking pressures of equilibrium valve in the oil return of the executive component the other end active chamber that returns from hydraulic fluid port B1 simultaneously; When manipulation equilibrium valve selector valve group 2 commutated to the right, its working principle was identical, and the fluid direction that enters executive component is opposite; When the valve group was in the diagram neutral position, first equilibrium valve 1 and second equilibrium valve 2 were in closed condition under the effect of A1, B1 oil circuit pressure and spring force, executive component can not glided or play voluntarily.
2, when manipulation Q type function selector valve group 3 commutated left, the off-load oil circuit of neutral passage 15 was cut off, and the first pressure oil P1 enters hydraulic fluid port A2 to executive component one end active chamber through parallel port 14.The oil return of the executive component the other end active chamber that returns from hydraulic fluid port B2 is simultaneously returned fuel tank through low-pressure channel 16 through hydraulic fluid port T; When handling 3 commutations to the right of Q type function selector valve group to a diagram left side during several the 3rd commutation position, the off-load oil circuit of neutral passage is cut off, and the first pressure oil P1 enters hydraulic fluid port B2 to executive component one end active chamber through parallel port 14.The oil return of the executive component the other end active chamber that returns from hydraulic fluid port A2 is returned fuel tank through low-pressure channel 16 through hydraulic fluid port T; When handling 3 commutations to the right of Q type function selector valve group to a diagram left side during several the 4th commutation position, the off-load oil circuit of neutral passage 15 is communicated with front and back valve group, fluid in the active chamber of executive component two ends is linked up through hydraulic fluid port T and oil circuit through low-pressure channel 16 through hydraulic fluid port A2, hydraulic fluid port B2, makes executive component two ends active chamber be in quick condition.When the valve group was in the diagram neutral position, the oil inlet and oil return road that leads to actuator port A2, B2 was cut off, and executive component is in halted state.
3, when operating hydraulically operated lock selector valve group 4 commutated left, the off-load oil circuit of neutral passage 15 was cut off, and the one-way valve that the first pressure oil P1 opens the hydraulic lock 1 that is built in the valve body through parallel port 14 enters executive component one end active chamber through hydraulic fluid port A3.The pressure oil that enters hydraulic lock 1 is simultaneously opened the one-way valve of hydraulic lock 2 through control oil channel, and the one-way valve that the oil return of the executive component the other end active chamber that returns from hydraulic fluid port B3 is opened through hydraulic lock 2 returns fuel tank through low-pressure channel 16 from hydraulic fluid port T; When operating hydraulically operated lock selector valve group 4 commutated to the right, its working principle was identical, and the fluid direction that enters executive component is opposite; When the valve group was in the diagram neutral position, hydraulic lock 1 and hydraulic lock 2 were in closed condition under the effect of hydraulic fluid port A3, B3 oil circuit pressure, and executive component can not glide or play voluntarily.
4, reset selector valve group 5 when commutating left when handling recoil, the off-load oil circuit of neutral passage 15 is cut off, and the first pressure oil P1 enters hydraulic fluid port A4 to executive component one end active chamber through parallel port 14.The oil return of the executive component the other end active chamber that returns from hydraulic fluid port B4 is simultaneously returned fuel tank through low-pressure channel 16 through hydraulic fluid port T; Reset selector valve group 5 when commutating to the right when handling recoil, and guiding valve adopts the spring mode reliably to locate, and the first pressure oil P1 enters hydraulic fluid port B4 to executive component one end active chamber through parallel port 14.The oil return of the executive component the other end active chamber that returns from hydraulic fluid port A4 is simultaneously returned fuel tank through low-pressure channel 16 through hydraulic fluid port T, when hydraulic fluid port B4 oil circuit pressure reaches recoil when resetting ejecting device default control pressure, ejecting device is opened, and reversing slide valve is replied the neutral position under action of reset spring; Required cracking pressure when regulating default control pressure and can change recoil and reset.When the valve group was in the diagram neutral position, the oil inlet and oil return road that leads to actuator port A4, B4 was cut off, and executive component is in halted state.
5, when manipulation timing reversal valve group 6 commutated left, the off-load oil circuit of neutral passage was cut off, and the first pressure oil P1 opens the one-way valve that is built in the unidirectional series flow control valve 1 in the valve body through parallel port 14 and enters executive component one end active chamber through hydraulic fluid port A5.The oil return of the executive component the other end active chamber that returns from hydraulic fluid port B5 is simultaneously returned fuel tank through low-pressure channel 16 from hydraulic fluid port T again by the restriction of unidirectional series flow control valve 2; When manipulation timing reversal valve group 6 commutated to the right, its working principle was identical, and the fluid direction that enters executive component is opposite; Regulate unidirectional series flow control valve 1 and unidirectional series flow control valve 2 respectively, can change the movement velocity of executive component two active chambers.When the valve group was in the diagram neutral position, the oil inlet and oil return road that leads to actuator port A5, B5 was cut off, and executive component is in halted state.
6, enter when handling pilot operated directional control valve group 8 and commutating left from hydraulic fluid port K1 when external control pressure oil, the off-load oil circuit of neutral passage 15 is cut off, and the first pressure oil P1 and second pressure oil P2 interflow are after parallel port 14 enters executive component one end active chamber through hydraulic fluid port A6.The oil return of the executive component the other end active chamber that returns from hydraulic fluid port B6 is simultaneously returned fuel tank through low-pressure channel 16 from hydraulic fluid port T; When external control pressure oil enters when handling pilot operated directional control valve group 8 and commutating to the right from hydraulic fluid port K2, its working principle is identical, and the fluid direction that enters executive component is opposite; When the external control pressure hydraulic fluid port K1 at guiding valve two ends and K2 all were in unloading condition, reversing slide valve kept the diagram neutral position under action of reset spring, and the oil inlet and oil return road that leads to actuator port A6, B6 is cut off, and executive component is in halted state.Because this valve group is the serial type oil channel structures, has cut off the asphalt channel that leads to the rear portion when this valve group is worked, so the valve group that the rear portion links to each other all can't be worked.
7, enter when handling air-actuated direction valve group 9 and commutating left from gas source interface K4 when the external compression air, the off-load oil circuit of neutral passage 15 is cut off, and the valve group that the pressure oil behind the interflow links to each other from the front portion enters executive component one end active chamber through parallel port 14 through hydraulic fluid port A7.The oil return of the executive component the other end active chamber that returns from hydraulic fluid port B7 is simultaneously returned fuel tank through low-pressure channel 16 from hydraulic fluid port T; When the external compression air enters when handling air-actuated direction valve group 9 and commutating to the right from gas source interface K3, its working principle is identical, and the fluid direction that enters executive component is opposite; When the pressurized air interface K3 that connects reversing cylinder and K4 all were in unloading condition, reversing slide valve kept the diagram neutral position under action of reset spring, was cut off towards the oil inlet and oil return road of actuator port A7, B7, and executive component is in halted state.
8, when handle overload, when repairing selector valve group 10 commutates left, the off-load oil circuit of neutral passage 15 is cut off, the valve group that the pressure oil behind the interflow links to each other from the front portion enters executive component one end active chamber through parallel port 14 through hydraulic fluid port A8.The oil return of the executive component the other end active chamber that returns from hydraulic fluid port B8 is simultaneously returned fuel tank through low-pressure channel 16 from hydraulic fluid port T; When the manipulation overload, when repairing selector valve group 10 commutates to the right, its working principle is identical, and the fluid direction that enters executive component is opposite; System oil-way can vibrate because of producing negative pressure state when executive component one end active chamber has little time fuel feeding in rapid movement, and the Fill valve that is installed in this moment in the hydraulic fluid port A8 oil circuit is opened repairing fast under the return pressure effect, eliminate oscillation phenomenon.When executive component the other end active chamber was subjected to load shock generation moment superpressure state, the overload valve 3 that is installed in the hydraulic fluid port B8 oil circuit was opened releases fast, closed when oil circuit pressure is lower than overload valve 3 set pressures, to guarantee security of system; When the valve group was in the diagram neutral position, the oil inlet and oil return road that leads to actuator port A8, B8 was cut off, and executive component is in halted state; Be installed in overload valve 3 set pressure as required in the valve group oil inlet and oil return road, when being higher than system's set pressure, make safety valve and use, make relief valve when being lower than system's set pressure and use.
Illustrate: 1 to 5 group of parallel connection type oil circuit selector valve group all can be handled use individually or simultaneously in this example; When parallel connection type oil circuit valve group is not all worked, the first pressure oil P1 is input to serial type oil circuit valve group through overload interflow valve group 7, because the oil-feed of serial type oil circuit valve group relies on neutral passage 15 inputs, current plate valve group has been cut off neutral passage 15 when operation, so all valve groups that the back links to each other all can not be worked.When the second pressure oil P2 was input to overload interflow valve group 7, no matter whether the parallel connection type oil circuit valve group that links to each other before valve switch operation all can handle the work of serial type oil circuit valve group; When the parallel connection type oil circuit of front in use, serial type oil circuit valve group has only the flow of the second pressure oil P2, when the parallel connection type oil circuit of front did not use, the oily flow that enters serial type oil circuit valve group was that the residual flow of the first pressure oil P1 adds that the flow of the second pressure oil P2 has played the effect at interflow.
Claims (3)
1. one kind high integrated multifunction multi-way valve, it is characterized in that: the two ends of described high integrated multifunction multi-way valve are arranged oiling valve group (1) and scavenger valve group or gap bridge valve group (11) respectively, intermediate arrangement equilibrium valve selector valve group (2), Q type function selector valve group (3), leading type hydraulic lock selector valve group (4), recoil reset the arbitrary valve group among selector valve group (5), timing reversal valve group (6), overload interflow valve group (7), pilot operated directional control valve group (8), air-actuated direction valve group (9) and overload, the repairing selector valve group (10) or the combination of a plurality of valve groups; On the valve body of above-mentioned each valve group mutually correspondence be provided with four public attachment holes, adopt four double threaded screws (12) to pass double threaded screw (12); Two ends connect as one by nut (13) tension; Be interconnected by the parallel port (14) of side, middle bit port (15) and low-pressure channel (16) between each valve group, form complete hydraulic control oil circuit.
2. high integrated multifunction multi-way valve according to claim 1 is characterized in that: described oiling valve group (1) adopts the oiling valve group with pressure controlled oiling valve group or band flow-dividing control.
3. high integrated multifunction multi-way valve according to claim 1 is characterized in that: the inside nominal diameter of pressing multi-way valve: 15mm, 22mm, 28mm, nominal flow rate is respectively: 100L/min, 180L/min, 280L/min, nominal pressure: 31.5MPa.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010292110212U CN201610873U (en) | 2010-02-05 | 2010-02-05 | Multifunctional highly-integrated multi-way valve |
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| Application Number | Priority Date | Filing Date | Title |
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| CN2010292110212U CN201610873U (en) | 2010-02-05 | 2010-02-05 | Multifunctional highly-integrated multi-way valve |
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| CN201610873U true CN201610873U (en) | 2010-10-20 |
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Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102562700A (en) * | 2012-01-20 | 2012-07-11 | 锦州市力特缸泵阀液压制造有限公司 | Combined-type multi-way reversing valve for coal-mine full-hydraulic underground drilling machine |
| CN103742682A (en) * | 2014-01-24 | 2014-04-23 | 浙江海宏液压科技股份有限公司 | Multiway valve for harvesters |
| CN103910311A (en) * | 2014-04-10 | 2014-07-09 | 安徽合力股份有限公司 | Hydraulic system of empty container stacking locomotive |
| CN104454727A (en) * | 2014-12-01 | 2015-03-25 | 山西北方机械制造有限责任公司 | Method for changing non-bridge-crossing-channel type valve to bridge-crossing-channel type valve |
| CN105114381A (en) * | 2015-07-27 | 2015-12-02 | 浙江海宏液压科技股份有限公司 | Converging multi-way valve |
| CN105987037A (en) * | 2015-02-15 | 2016-10-05 | 徐工集团工程机械股份有限公司 | Control valve of proportional multi-way valve, control linkage, proportional multi-way valve and crane |
| CN108266418A (en) * | 2018-03-23 | 2018-07-10 | 泸州众大科技液压件有限公司 | A kind of sealing structure between combined sheet type multiple directional control valve valve block |
| CN114729516A (en) * | 2019-11-06 | 2022-07-08 | 法斯特股份公司 | Integrated multi-connection hydraulic unit |
-
2010
- 2010-02-05 CN CN2010292110212U patent/CN201610873U/en not_active Expired - Fee Related
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102562700A (en) * | 2012-01-20 | 2012-07-11 | 锦州市力特缸泵阀液压制造有限公司 | Combined-type multi-way reversing valve for coal-mine full-hydraulic underground drilling machine |
| CN102562700B (en) * | 2012-01-20 | 2014-10-01 | 锦州市力特缸泵阀液压制造有限公司 | Combined-type multi-way reversing valve for coal-mine full-hydraulic underground drilling machine |
| CN103742682A (en) * | 2014-01-24 | 2014-04-23 | 浙江海宏液压科技股份有限公司 | Multiway valve for harvesters |
| CN103910311A (en) * | 2014-04-10 | 2014-07-09 | 安徽合力股份有限公司 | Hydraulic system of empty container stacking locomotive |
| CN104454727A (en) * | 2014-12-01 | 2015-03-25 | 山西北方机械制造有限责任公司 | Method for changing non-bridge-crossing-channel type valve to bridge-crossing-channel type valve |
| CN105987037A (en) * | 2015-02-15 | 2016-10-05 | 徐工集团工程机械股份有限公司 | Control valve of proportional multi-way valve, control linkage, proportional multi-way valve and crane |
| CN105987037B (en) * | 2015-02-15 | 2018-07-17 | 徐工集团工程机械股份有限公司 | Control valve, control connection, proportional multi-way valve and the crane of proportional multi-way valve |
| CN105114381A (en) * | 2015-07-27 | 2015-12-02 | 浙江海宏液压科技股份有限公司 | Converging multi-way valve |
| CN105114381B (en) * | 2015-07-27 | 2017-03-01 | 浙江海宏液压科技股份有限公司 | Interflow banked direction control valves |
| CN108266418A (en) * | 2018-03-23 | 2018-07-10 | 泸州众大科技液压件有限公司 | A kind of sealing structure between combined sheet type multiple directional control valve valve block |
| CN114729516A (en) * | 2019-11-06 | 2022-07-08 | 法斯特股份公司 | Integrated multi-connection hydraulic unit |
| CN114729516B (en) * | 2019-11-06 | 2023-10-31 | 法斯特股份公司 | Integrated multi-connection hydraulic group |
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