CN203670337U - Load-sensitive electric proportional multi-way valve - Google Patents
Load-sensitive electric proportional multi-way valve Download PDFInfo
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- CN203670337U CN203670337U CN201320840681.3U CN201320840681U CN203670337U CN 203670337 U CN203670337 U CN 203670337U CN 201320840681 U CN201320840681 U CN 201320840681U CN 203670337 U CN203670337 U CN 203670337U
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Abstract
The utility model relates to a load-sensitive electric proportional multi-way valve. According to the load-sensitive electric proportional multi-way valve, loops can work with different loads, energy is saved, and environmental pollution is reduced. According to the technical scheme, the load-sensitive electric proportional multi-way valve comprises a main oil path communicated with two gear pumps P1 and P2, a lifting loop, inclined units and accessory units, a logical direction valve, a two-way solenoid valve, a proportional electric overflow valve and a two-way hydraulic control reversing valve. The lifting loop is connected to the main oil path through electronic proportion pressure compensation flow control valves, the inclined units and the accessory units are connected to the main oil path through electronic proportion pressure compensation flow control valves, the logical direction valve is connected to the main oil path, the two-way solenoid valve and the proportional electric overflow valve are connected to an oil inlet of the logical direction valve, and the two-way hydraulic control reversing valve is used for controlling the gear pump P2 to supply oil to the main oil path or not. The load-sensitive electric proportional multi-way valve is used for the technical field of 5-10-ton forklift hydraulic system control valves.
Description
Technical field
The utility model relates to a kind of multi-way valve, and particularly a kind of load-sensitive electricity proportional multi-way valve, is mainly applicable to 5-10 ton forklift HYDRAULIC CONTROL SYSTEM valve technology field.
Background technique
Multiple directional control valve is that to have two or more reversing slide valves be the combination brake switch and proporting of main body.This product can be widely used in various engineering machinery, farm machinery and mining machinery.The executive component that multiple directional control valve will be controlled has two at least, due to the required working flow difference of different executive components, and oil sources need to configure according to peak rate of flow, like this in the time only having an executive component action or executive component speed lower, unnecessary fluid can only high pressure unloading, cause thus loss function, heating in a large number, totally unfavorable to the life-span of system and element.People are more and more higher to energy-conservation requirement in recent years, and the energy-conserving and environment-protective of hydraulic system are required also progressively improving.
The flow needing when 5-10 ton forklift hoists both at home and abroad is at present very large, the flow needing when inclination or the action of other accessories is less, what but 5-10 ton forklift was conventional is the quantitative system that manually-operable multiple directional control valve is joined two gear pumps, Dual-pump flow-converging when action, when inclination or the action of other accessories, because of the oil of need very little, metering pump provides unnecessary oil sources often with the pressure off-load of safety valve setting, cause like this engine idle work easily to stop working because moment of torsion is less than normal, energy waste is very big, and this manually operated multiple directional control valve steering force is large, reversing impact is large, control performance is poor, but simple in structure, cost is low.But more and more higher along with scientific and technical progress and people's requirement, manually operated valve can not meet people's requirement; In addition, in the time that there is fine motion requirement accurately in actuator, such scheme is difficult to realize.
Summary of the invention
The technical problems to be solved in the utility model is: provide for the problem of above-mentioned existence the load-sensitive electricity proportional multi-way valve that a kind of manual dexterity, precision are high, can receive the single or multiple control command signals of controller simultaneously, make the each loop of multi-way valve with different loaded work pieces, energy saving, reduces environmental pollution.
The technological scheme that the utility model adopts is: load-sensitive electricity proportional multi-way valve, it is characterized in that: it comprises dynamic load induction pressure recuperation valve, safety valve I and pressure compensated flow modulating valve I, the wherein filler opening connection teeth wheel pump P1 of dynamic load induction pressure recuperation valve, an oil outlet connects commutator CF mouth, another oil outlet connects multi-way valve working connection, and the LS signal hydraulic fluid port of this recuperation valve is communicated with commutator LS mouth and safety valve I filler opening simultaneously, and safety valve I oil outlet is communicated with return opening D; On described working connection, be connected with on the one hand hoisting circuit and hydraulically-controlled one-way valve I in turn, the outlet of this hydraulically-controlled one-way valve I connects respectively the decline loop that hoist hydraulic fluid port A1 and oil outlet are communicated with oil return inlet T, be connected with respectively connection and accessory connection through electronics ratio pressure compensating flowrate control valve V on the one hand, be communicated with oil return inlet T through logical direction valve on the other hand; The oil drain out of described hoisting circuit is connected with the electronic relief valve of proportional-type that hydraulically-controlled one-way valve III and oil outlet are communicated with oil return inlet T on the one hand in turn, is communicated with on the other hand through pressure compensated flow modulating valve II with oil return inlet T; The oil drain out of described electronics ratio pressure compensating flowrate control valve V is communicated with oil return inlet T through the electronic relief valve of proportional-type on the one hand, is communicated with on the other hand through pressure compensated flow modulating valve III with oil return inlet T; The filler opening that described logical direction valve is communicated with working connection is communicated with through the electronic relief valve filler opening of hydraulically-controlled one-way valve IV and proportional-type on the one hand, is communicated with on the other hand through two-way electromagnetic valve with return opening D; Pressure compensated flow modulating valve I filler opening connection teeth wheel pump P2, an oil outlet is communicated with brake valve entrance BR, another oil outlet is communicated with working connection through hydraulically-controlled one-way valve II on the one hand, be communicated with oil return inlet T through two-way pilot operated directional control valve on the other hand, the control port C of described two-way pilot operated directional control valve is communicated with the oil drain out of hoisting circuit.
Described hoisting circuit is formed in parallel by electronics ratio pressure compensating flowrate control valve I and electronics ratio pressure compensating flowrate control valve II.
Route electronic ratio pressure compensating flowrate control valve III is returned in described decline and electronics ratio pressure compensating flowrate control valve IV is formed in parallel.
Described inclination connection comprises the three-way four-position solenoid directional control valve I being communicated with electronics ratio pressure compensating flowrate control valve V oil outlet, the oil return port of this selector valve is communicated with oil return inlet T, actuator port A is communicated with inclination hydraulic fluid port A2 through equilibrium valve, actuator port B is communicated with inclination hydraulic fluid port B2 on the one hand, be communicated with oil return inlet T through safety valve II on the one hand, be communicated with the control port of equilibrium valve on the other hand.
Described accessory connection comprises the accessory selector valve being communicated with electronics ratio pressure compensating flowrate control valve V oil outlet, two actuator ports of this accessory selector valve are communicated with two accessory hydraulic fluid ports respectively, and on one of them actuator port, be connected with accessory safety valve, the oil outlet of this accessory safety valve is communicated with oil return inlet T.
Described accessory has been allied the communists two groups.
The beneficial effects of the utility model are: 1, the utility model arranges two-way pilot operated directional control valve, two-way electromagnetic valve, logical direction valve and the electronic relief valve of proportional-type on multi-way valve oil circuit, make its two pumps (P1, P2) interflow work in the time that execution hoists action, single pump work when other actions, another pump off-load, can not produce unnecessary power, more meet the requirement of energy-conserving and environment-protective.2, process engine rotational speed signal by controller, what add the electronic relief valve of proportional-type should be used for realizing anti-idling flameout function; 3, adopt electric proportional control to replace manually-operable of the prior art, the large impact while having avoided commutation, system having been brought also improves a lot simultaneously in control accuracy; 4, this multi-way valve is integral valve, and volume is little, power is large, simplifies pipeline and connects, and has effectively reduced the leakage point of hydraulic system, has reduced the pollution to environment.
Accompanying drawing explanation
Fig. 1 is hydraulic schematic diagram of the present utility model.
Embodiment
As shown in Figure 1, the present embodiment comprises dynamic load induction pressure recuperation valve 11, safety valve I 1 and pressure compensated flow modulating valve I 12; The wherein filler opening connection teeth wheel pump P1 of dynamic load induction pressure recuperation valve 11, an oil outlet connects commutator CF mouth, another oil outlet connects multi-way valve working connection, and the LS signal hydraulic fluid port of this recuperation valve is communicated with commutator LS mouth and safety valve I 1 filler opening simultaneously, and safety valve I 1 oil outlet is communicated with return opening D; On described working connection, be connected with on the one hand hoisting circuit and hydraulically-controlled one-way valve I 4 in turn, the outlet of this hydraulically-controlled one-way valve I connects respectively the decline loop that hoist hydraulic fluid port A1 and oil outlet are communicated with oil return inlet T, be connected with respectively connection and accessory connection through electronics ratio pressure compensating flowrate control valve V 21 on the one hand, be communicated with oil return inlet T through logical direction valve 15 on the other hand; The oil drain out of described hoisting circuit is connected with the electronic relief valve 18 of proportional-type that hydraulically-controlled one-way valve III 16 and oil outlet are communicated with oil return inlet T on the one hand in turn, is communicated with on the other hand through pressure compensated flow modulating valve II 19 with oil return inlet T; The oil drain out of described electronics ratio pressure compensating flowrate control valve V 21 is communicated with oil return inlet T through the electronic relief valve 18 of proportional-type on the one hand, is communicated with on the other hand through pressure compensated flow modulating valve III 20 with oil return inlet T; The filler opening that described logical direction valve 15 is communicated with working connection is communicated with through electronic relief valve 18 filler openings of hydraulically-controlled one-way valve IV 17 and proportional-type on the one hand, is communicated with on the other hand through two-way electromagnetic valve 25 with return opening D; Pressure compensated flow modulating valve I 12 filler opening connection teeth wheel pump P2, an oil outlet is communicated with brake valve entrance BR, another oil outlet is communicated with working connection through hydraulically-controlled one-way valve II 13 on the one hand, be communicated with oil return inlet T through two-way pilot operated directional control valve 14 on the other hand, the control port C of described two-way pilot operated directional control valve 14 is communicated with the oil drain out of hoisting circuit.
Because the international Single Electron ratio pressure compensating flowrate control valve flow of producing is less than normal at present, can not meet the demand of the oil circuit flow that hoists, therefore, described in the present embodiment, hoisting circuit is formed in parallel by electronics ratio pressure compensating flowrate control valve I 2 and electronics ratio pressure compensating flowrate control valve II 3, and the oil drain out of two flow control valves is all connected to the filler opening of hydraulically-controlled one-way valve III 16; Equally, the route electronic ratio pressure compensating flowrate control valve III 5 that declines back and electronics ratio pressure compensating flowrate control valve IV 6 are formed in parallel, and the entrance of two flow control valves is all communicated with the oil outlet of hydraulically-controlled one-way valve III 16, and outlet is all communicated with oil return inlet T.
Described inclination connection comprises the three-way four-position solenoid directional control valve I 22 being communicated with electronics ratio pressure compensating flowrate control valve V 21 oil outlets, the oil return port of this selector valve is communicated with oil return inlet T, actuator port A is communicated with inclination hydraulic fluid port A2 through equilibrium valve 7, actuator port B is communicated with inclination hydraulic fluid port B2 on the one hand, be communicated with oil return inlet T through safety valve II 8 on the one hand, be communicated with the control port of equilibrium valve 7 on the other hand.
Described in the present embodiment, accessory has been allied the communists two groups, wherein one group is the three-way four-position solenoid directional control valve II 23 being communicated with electronics ratio pressure compensating flowrate control valve V 21 oil outlets, the oil return port of this selector valve is communicated with oil return inlet T, one of them actuator port is communicated with accessory hydraulic fluid port A3, another actuator port is communicated with accessory hydraulic fluid port B3 on the one hand, is communicated with on the other hand through deadweight safety valve III 9 with oil return inlet T; The three-way four-position solenoid directional control valve III 24 of another group for being communicated with electronics ratio pressure compensating flowrate control valve V 21 oil outlets, the oil return port of this selector valve is communicated with oil return inlet T, one of them actuator port is communicated with accessory hydraulic fluid port A4, another actuator port is communicated with accessory hydraulic fluid port B4 on the one hand, is communicated with on the other hand through deadweight safety valve IV 10 with oil return inlet T.
While turning to, hydraulic oil preferentially enters commutator CF mouth successively after gear pump P1 and dynamic load induction pressure recuperation valve 11, and realization turns to; In the time turning to oil circuit pressure excessive, from safety valve I 1 draining.
When braking, hydraulic oil enters brake valve entrance BR successively after gear pump P2 and pressure compensated flow modulating valve I 12, realizes braking.
Two-way electromagnetic valve 25 has two states, when any one or several valve in five electronics ratio pressure compensating flowrate control valves obtain when electric, two-way electromagnetic valve 25 obtains electric in closed state, then logical direction valve 15 internal control oil requires divide two-way by hydraulically-controlled one-way valve IV 17, the electronic relief valve 18 of the proportional-type of leading up to, lead up to pressure compensated flow modulating valve III 20, in the time of pressure that the pressure of oil circuit is set higher than the electronic relief valve 18 of proportional-type from electronic relief valve 18 oil sump tanks of proportional-type (safety effect), when pressure that pressure is set lower than the electronic relief valve 18 of proportional-type from pressure compensated flow modulating valve III 20 oil sump tanks: in the time that five electronics ratio pressure compensating flowrate control valves all must not electricity, two-way electromagnetic valve 25 is in on-state, logical direction valve 15 internal control oil are by the direct oil sump tank of two-way electromagnetic valve 25.
The control port C of two-way pilot operated directional control valve 14 is only hoisting oil circuit A1 mouth induced pressure when feedback, and two-way pilot operated directional control valve 14 disconnects, and gear pump P2 working oil is to the working connection state that hoists; In the time tilting connection and accessory connection or fork truck meta attonity, what control port C connect is pressure compensated flow modulating valve II 19 and fuel tank, does not have pressure signal (without oil sources), and two-way pilot operated directional control valve 14 is connected, the oil of gear pump P2 is by 14 off-loads of two-way pilot operated directional control valve, and crushing is very little.
The electronic relief valve 18 of proportional-type, as system main safety valve, the Maximum operating pressure of system is controlled thus.Realize anti-idling flameout function: program setting engine speed 750r/min(idling) time, control current signal to 18 1 of the electronic relief valves of proportional-type, the electronic relief valve 18 of control ratio type is opened, the electronic relief valve 18 of proportional-type is opened size and is had influence on its pressure setting under this current signal, electric current is larger, the pressure that the electronic relief valve 18 of proportional-type is set is less, and working oil path prevents engine misses with very safe pressure off-load.In the time that engine speed is greater than the 750r/min of program setting, program is the unlatching of the electronic relief valve 18 of control ratio type not, and function now realizes the same with common safety valve.
For logical direction valve 5, supposing that oil mass that gear pump provides is greater than hoists or the oil (load flow size in the control of electronics ratio pressure compensating flowrate control valve openings of sizes) of needs when inclination or accessory state, the unnecessary oil of gear pump in this time can ring off by logical direction valve 15, logical direction valve 15 is guiding valves, variable throttling, in process, the inlet pressure of electronics ratio pressure compensating flowrate control valve V 21 should be the pressure loss of induced pressure+electronics Proportional valve, the loss ringing off from valve 15 is the pressure loss of induced pressure+electronics Proportional valve, but domestic current system, unnecessary oil is that the crushing of setting according to overload valve releases, in the time that system pressure is too high, the electronic relief valve 18 of logical direction valve 15 and proportional-type plays guide's overflow effect.
When five electronics ratio pressure compensating flowrate control valves all must not when electricity, the oil of gear pump P1 arrives the filler opening of logical direction valve 15 after dynamic load induction pressure recuperation valve 11, in this process, two-way electromagnetic valve 25 must not be electric, normal open, when the pressure drop that the filler opening flow of logical direction valve 15 produces through the restriction of logical direction valve 15 the insides is greater than the very little spring force of logical direction valve 15, spool moves to left, logical direction valve 15 is connected, and the oil of gear pump P1 is oil sump tank after dynamic load induction pressure recuperation valve 11, logical direction valve 15 and oil return inlet T successively; The oil of gear pump P2 is oil sump tank after pressure compensated flow modulating valve I 12, two-way pilot operated directional control valve 14 and oil return inlet T successively, two-way pilot operated directional control valve 14 normal opens herein, the control port C place that is two-way pilot operated directional control valve 14 is non-loaded without oil, spring force makes spool in normal open state, in this process, two blowback roads generation crushings are very little, energy-saving and emission-reduction.
When electronics ratio pressure compensating flowrate control valve I 2 and electronics ratio pressure compensating flowrate control valve II 3 when electric, state hoists, the oil of gear pump P1 enters working connection through dynamic load induction pressure recuperation valve 11, now, the control port C of two-way pilot operated directional control valve 14 has load, and this induced pressure overcomes the spring force of two-way pilot operated directional control valve 14, spool moves to right, two-way pilot operated directional control valve 14 is closed, the oil of gear pump P2 also enters working connection after hydraulically-controlled one-way valve IV 17, oil interflow with gear pump P1, and after electronics ratio pressure compensating flowrate control valve I 2 and electronics ratio pressure compensating flowrate control valve II 3, arrive by hydraulically-controlled one-way valve I 4 the hydraulic fluid port A1 that hoists, provide stable flow according to the size of Proportional valve opening to A1 mouth, the unnecessary oil that gear pump P1 and P2 provide, let out oil sump tank according to the crushing of induced pressure+pressure compensator by logical direction valve 15, at present under domestic this operating mode, it is the pressure loss oil sump tank of setting according to overload valve that gear pump P1 and P2 pump provide unnecessary oil, save a lot of energy herein.When the state overburden that hoists, when working oil path overpressure, the electronic relief valve 18 of proportional-type plays safety valve effect (similar with common overload valve).
When electronics ratio pressure compensating flowrate control valve III 5 and electronics ratio pressure compensating flowrate control valve IV 6 when electric, the state that declines, the oil (oil that the cylinder the inside that hoists when hoisting is filled) of A1 mouth the inside by two electronics ratio pressure compensating flowrate control valve III, IV with stable flow velocity oil sump tank.The oil of gear pump P1 enters working connection through dynamic load induction pressure recuperation valve 11, and by the direct oil sump tank of logical direction valve 15, the oil of gear pump P2 is through two-way pilot operated directional control valve 14 also direct oil sump tank.
When electronics ratio pressure compensating flowrate control valve V 21 when electric, the control port C place of two-way pilot operated directional control valve 14 is non-loaded without oil, spring force makes two-way pilot operated directional control valve 14 in on-state, and the oil of gear pump P2 is direct oil sump tank after pressure compensated flow modulating valve I 12 and two-way pilot operated directional control valve 14.The oil of gear pump P1 is through electronics ratio pressure compensating flowrate control valve V 21, and to equipment district, gear pump P1 provides stable flow according to hydraulic fluid port A2, B2 or A3, B3 or A4, B4 load, and unnecessary oil is through logical direction valve 15 oil sump tanks.The oil of this process middle gear pump P2 is with very little pressure loss off-load, energy saving.
Claims (6)
1. a load-sensitive electricity proportional multi-way valve, it is characterized in that: it comprises dynamic load induction pressure recuperation valve (11), safety valve I (1) and pressure compensated flow modulating valve I (12), the wherein filler opening connection teeth wheel pump P1 of dynamic load induction pressure recuperation valve (11), an oil outlet connects commutator CF mouth, another oil outlet connects multi-way valve working connection, and the LS signal hydraulic fluid port of this recuperation valve is communicated with commutator LS mouth and safety valve I (1) filler opening simultaneously, and safety valve I (1) oil outlet is communicated with return opening D; On described working connection, be connected with on the one hand hoisting circuit and hydraulically-controlled one-way valve I (4) in turn, the outlet of this hydraulically-controlled one-way valve I connects respectively the decline loop that hoist hydraulic fluid port A1 and oil outlet are communicated with oil return inlet T, be connected with respectively connection and accessory connection through electronics ratio pressure compensating flowrate control valve V (21) on the one hand, be communicated with oil return inlet T through logical direction valve (15) on the other hand; The oil drain out of described hoisting circuit is connected with the electronic relief valve of proportional-type (18) that hydraulically-controlled one-way valve III (16) and oil outlet are communicated with oil return inlet T on the one hand in turn, is communicated with on the other hand through pressure compensated flow modulating valve II (19) with oil return inlet T; The oil drain out of described electronics ratio pressure compensating flowrate control valve V (21) is communicated with oil return inlet T through the electronic relief valve of proportional-type (18) on the one hand, is communicated with on the other hand through pressure compensated flow modulating valve III (20) with oil return inlet T; The filler opening that described logical direction valve (15) is communicated with working connection is communicated with the electronic relief valve of proportional-type (18) filler opening through hydraulically-controlled one-way valve IV (17) on the one hand, is communicated with on the other hand through two-way electromagnetic valve (25) with return opening D; Pressure compensated flow modulating valve I (12) filler opening connection teeth wheel pump P2, an oil outlet is communicated with brake valve entrance BR, another oil outlet is communicated with working connection through hydraulically-controlled one-way valve II (13) on the one hand, be communicated with oil return inlet T through two-way pilot operated directional control valve (14) on the other hand, the control port C of described two-way pilot operated directional control valve (14) is communicated with the oil drain out of hoisting circuit.
2. load-sensitive electricity proportional multi-way valve according to claim 1, is characterized in that: described hoisting circuit is formed in parallel by electronics ratio pressure compensating flowrate control valve I (2) and electronics ratio pressure compensating flowrate control valve II (3).
3. load-sensitive electricity proportional multi-way valve according to claim 1 and 2, is characterized in that: route electronic ratio pressure compensating flowrate control valve III (5) is returned in described decline and electronics ratio pressure compensating flowrate control valve IV (6) is formed in parallel.
4. load-sensitive electricity proportional multi-way valve according to claim 1 and 2, it is characterized in that: described inclination connection comprises the three-way four-position solenoid directional control valve I (22) being communicated with electronics ratio pressure compensating flowrate control valve V (21) oil outlet, the oil return port of this selector valve is communicated with oil return inlet T, actuator port A is communicated with inclination hydraulic fluid port A2 through equilibrium valve (7), actuator port B is communicated with inclination hydraulic fluid port B2 on the one hand, be communicated with oil return inlet T through safety valve II (8) on the one hand, be communicated with the control port of equilibrium valve (7) on the other hand.
5. load-sensitive electricity proportional multi-way valve according to claim 1 and 2, it is characterized in that: described accessory connection comprises the accessory selector valve being communicated with electronics ratio pressure compensating flowrate control valve V (21) oil outlet, two actuator ports of this accessory selector valve are communicated with two accessory hydraulic fluid ports respectively, and on one of them actuator port, be connected with accessory safety valve, the oil outlet of this accessory safety valve is communicated with oil return inlet T.
6. load-sensitive electricity proportional multi-way valve according to claim 5, is characterized in that: described accessory has been allied the communists two groups.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320840681.3U CN203670337U (en) | 2013-12-19 | 2013-12-19 | Load-sensitive electric proportional multi-way valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320840681.3U CN203670337U (en) | 2013-12-19 | 2013-12-19 | Load-sensitive electric proportional multi-way valve |
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| Publication Number | Publication Date |
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| CN203670337U true CN203670337U (en) | 2014-06-25 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201320840681.3U Withdrawn - After Issue CN203670337U (en) | 2013-12-19 | 2013-12-19 | Load-sensitive electric proportional multi-way valve |
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| CN (1) | CN203670337U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103671335A (en) * | 2013-12-19 | 2014-03-26 | 杭叉集团股份有限公司 | Load-sensitive electric proportional multi-loop valve |
| CN104315107A (en) * | 2014-10-17 | 2015-01-28 | 绍兴金道齿轮箱有限公司 | Hydraulic drive gearbox |
| CN113757203A (en) * | 2021-09-13 | 2021-12-07 | 徐工集团工程机械股份有限公司科技分公司 | Loader electric control hydraulic system and loader |
-
2013
- 2013-12-19 CN CN201320840681.3U patent/CN203670337U/en not_active Withdrawn - After Issue
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103671335A (en) * | 2013-12-19 | 2014-03-26 | 杭叉集团股份有限公司 | Load-sensitive electric proportional multi-loop valve |
| CN104315107A (en) * | 2014-10-17 | 2015-01-28 | 绍兴金道齿轮箱有限公司 | Hydraulic drive gearbox |
| CN113757203A (en) * | 2021-09-13 | 2021-12-07 | 徐工集团工程机械股份有限公司科技分公司 | Loader electric control hydraulic system and loader |
| CN113757203B (en) * | 2021-09-13 | 2022-04-15 | 徐工集团工程机械股份有限公司科技分公司 | Loader electric control hydraulic system and loader |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20140625 Effective date of abandoning: 20151202 |
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| C25 | Abandonment of patent right or utility model to avoid double patenting |