CN113757203A - Loader electric control hydraulic system and loader - Google Patents
Loader electric control hydraulic system and loader Download PDFInfo
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- CN113757203A CN113757203A CN202111068003.5A CN202111068003A CN113757203A CN 113757203 A CN113757203 A CN 113757203A CN 202111068003 A CN202111068003 A CN 202111068003A CN 113757203 A CN113757203 A CN 113757203A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/025—Pressure reducing valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/08—Servomotor systems incorporating electrically operated control means
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- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention discloses an electric control hydraulic system of a loader and the loader, belonging to the technical field of loaders, wherein the electric control hydraulic system of the loader comprises a hydraulic device and an electric control device, and the electric control device is connected with the hydraulic device in parallel; in the manual mode, the loader is controlled by the hydraulic device; under the electric control mode, the loader is controlled by the electric control device and the hydraulic device together, so that the electric control can be realized under the condition of not changing the integral structure of the conventional hydraulic device, and the remote control and unmanned performance of the loader can be met; all the improved parts are made in a domestic manner, so that the manufacturing cost is reduced, and the dependence on an inlet part is eliminated.
Description
Technical Field
The invention belongs to the technical field of loaders, and particularly relates to an electric control hydraulic system of a loader and the loader.
Background
In the prior art, an electronic control multi-way valve and an electronic control steering gear are mainly adopted for the electronic control of a loader hydraulic system, and main components such as the electronic control multi-way valve, the electronic control steering gear, a flow amplification valve and an electric handle are imported components and are all loader fully-variable hydraulic systems, so that the cost is high, and the domestic technology is still not mature. According to the current situation of the domestic loader, along with the rapid development of the informatization technology, the requirements for engineering machinery for remote control and unmanned operation are gradually increased, but the prior art still depends on imported elements. The hydraulic system of the domestic loader is still mainly a quantitative hydraulic system, and the existing electric control hydraulic system is not suitable.
Disclosure of Invention
In order to overcome the defects in the prior art, the invention provides an electric control hydraulic system of a loader and the loader, which can realize electric control under the condition of not changing the integral structure of the existing hydraulic device and can meet the requirement of remote control and no humanization of the loader.
In order to achieve the purpose, the technical scheme adopted by the invention is as follows:
in a first aspect, an electric control hydraulic system of a loader is provided, which comprises a hydraulic device and an electric control device, wherein the electric control device is connected with the hydraulic device in parallel; in the manual mode, the loader is controlled by the hydraulic device; in the electric control mode, the loader is controlled by the electric control device and the hydraulic device together.
Furthermore, the hydraulic device comprises a gear pump, a multi-way valve, a flow amplifying valve, a pilot oil source valve and a steering gear, and the electric control device comprises an electric proportional pressure reducing valve and a flow control valve; the oil outlet of the gear pump is respectively communicated with oil inlets of the multi-way valve, the flow amplifying valve, the pilot oil source valve, the steering gear and the flow control valve; the oil outlet of the pilot oil source valve is respectively communicated with the pilot valve and the oil inlets of the electric proportional reducing valves, and is communicated with the multi-way valve through the pilot valve and the electric proportional reducing valves; the diverter is connected with the flow control valve in parallel and then communicated with the flow amplification valve.
Further, a port a1P of the electro proportional pressure reducing valve is communicated with a port a1 of a pilot valve, and a port a1T of the electro proportional pressure reducing valve is communicated with a port a1 of a multi-way valve; the port a2P of the electro-proportional pressure reducing valve is communicated with the port a2 of the pilot valve, and the port a2T of the electro-proportional pressure reducing valve is communicated with the port a2 of the multi-way valve; the port b1P of the electro-proportional pressure reducing valve is communicated with the port b1 of the pilot valve, and the port b1T of the electro-proportional pressure reducing valve is communicated with the port b1 of the multi-way valve; the port b2P of the electro-proportional pressure reducing valve is communicated with the port b2 of the pilot valve, and the port b2T of the electro-proportional pressure reducing valve is communicated with the port b2 of the multi-way valve; in a manual mode, the electric proportional pressure reducing valve cannot be electrified, the port a1P is communicated with the port a1T, the port a2P is communicated with the port a2T, the port b1P is communicated with the port b1T, the port b2P is communicated with the port b2T, the pilot valve is connected with the electric proportional pressure reducing valve in series, and the multi-way valve is controlled by the pilot valve; in the electric control mode, the electric proportional pressure reducing valve is electrified, the pilot valve is cut off, and the multi-way valve is controlled by the electric proportional pressure reducing valve.
Furthermore, an R1 port of the flow amplifying valve is respectively communicated with an R port of the steering gear and an R2 port of the flow control valve; the L1 port of the flow amplifying valve is respectively communicated with the L port of the steering gear and the L2 port of the flow control valve; in the manual mode, the flow control valve is not powered, and the steering is controlled by the steering gear; in the electric control mode, the flow control valve is energized and controls steering.
Furthermore, the flow control valve comprises an electric proportional valve and a pressure compensator, an oil inlet of the electric proportional valve is communicated with a control cavity of the pressure compensator, and an oil outlet of the electric proportional valve is connected with a spring cavity of the pressure compensator.
Furthermore, when the flow control valve is not electrified, no flow passes through the flow control valve, and all pilot oil is supplied to the steering gear and the pilot oil source valve; when the steering wheel turns to the right, the electric proportional valve is electrified to be opened, hydraulic oil discharged from the gear pump passes through the electric proportional valve to enable the oil inlet and the oil outlet of the electric proportional valve to generate pressure difference to act on two ends of the pressure compensator respectively, and the output flow is as follows:
wherein q is the flow passing through the electric proportional valve; cdIs a flow coefficient, is a constant; AT is the opening area of the electro proportional valve; delta p is the pressure difference of an oil inlet and an oil outlet of the electro proportional valve; ρ is the hydraulic oil density.
Furthermore, the flow control valve also comprises a three-position four-way electromagnetic directional valve, when the steering is performed on the right, an L2 port of the flow control valve is electrified, at the moment, an oil inlet is formed at a P port of the three-position four-way electromagnetic directional valve, and the oil returns from an A port through a flow amplifying valve control cavity and an B port; when the steering wheel turns left, the R2 port of the flow control valve is electrified, at the moment, the oil enters the P port of the three-position four-way electromagnetic directional valve, and the oil returns through the A port by the control cavity of the flow amplifying valve after the oil exits from the B port.
Further, the automatic control device also comprises a switch valve for switching a manual mode and an electric control mode.
Furthermore, the gear pump comprises a pilot pump, a steering pump and a working pump, and an oil outlet of the pilot pump is respectively communicated with oil inlets of a pilot oil source valve, a steering gear and a flow control valve; an oil outlet of the steering pump is communicated with an oil inlet of the flow amplifying valve; and the oil outlet of the working pump is respectively communicated with the PF port of the flow amplifying valve and the oil inlet of the multi-way valve.
In a second aspect, a loader is provided, which is equipped with the electrically controlled hydraulic system of the loader of the first aspect.
Compared with the prior art, the invention has the following beneficial effects:
(1) according to the invention, a set of electric control device is connected in parallel with the existing hydraulic device, and in a manual mode, the loader is controlled by the hydraulic device; under the electric control mode, the loader is controlled by the electric control device and the hydraulic device together, so that the control of each action program of the whole machine is realized, the electric control can be realized under the condition of not changing the integral structure of the existing hydraulic device, and the remote control and the unmanned performance of the loader can be simultaneously met;
(2) all the improved parts of the invention realize localization, reduce the manufacturing cost and get rid of the dependence on imported parts.
Drawings
FIG. 1 is a schematic system structure diagram of an electrically controlled hydraulic system of a loader according to an embodiment of the present invention;
fig. 2 is a system configuration diagram of the flow control valve in fig. 1.
Detailed Description
The invention is further described below with reference to the accompanying drawings. The following examples are only for illustrating the technical solutions of the present invention more clearly, and the protection scope of the present invention is not limited thereby.
The first embodiment is as follows:
as shown in fig. 1 and 2, an electrically controlled hydraulic system of a loader comprises a hydraulic device and an electric control device, wherein the electric control device is connected with the hydraulic device in parallel; in the manual mode, the loader is controlled by the hydraulic device; in the electric control mode, the loader is controlled by the electric control device and the hydraulic device together.
The hydraulic device comprises a gear pump 1, a multi-way valve 2, a flow amplifying valve 3, a pilot valve 4, a pilot oil source valve 5 and a steering gear 6, and the electric control device comprises an electric proportional pressure reducing valve 7 and a flow control valve 8; and the switch valve is used for switching a manual mode and an electric control mode, the switch valve is in the manual mode when closed, a pilot valve 4 and a steering gear 6 are operated by a driver, and the electric control of the hydraulic system can be realized when the switch valve is opened.
The gear pump 1 is a triple pump and comprises a pilot pump, a steering pump and a working pump, wherein an oil outlet of the working pump is respectively communicated with a PF port of the flow amplifying valve 3 and an oil inlet of the multi-way valve 2; an oil outlet of the steering pump is communicated with an oil inlet of the flow amplifying valve 3; the oil outlet of the pilot pump is respectively communicated with the oil inlets of the pilot oil source valve 5, the steering gear 6, the flow control valve 8 and the overflow valve 10, and the overflow valve 10 determines the oil supply pressure of the flow control valve 8 and the steering gear 6; the flow control valve 8 and the steering gear 6 are connected in parallel to jointly control the reversing of the flow amplification valve 8 to realize the steering of the whole steering gear, specifically, an L port of the steering gear 6 and an L2 port of the flow control valve 8 are connected in parallel and simultaneously connected with an L1 port of the flow amplification valve, and an R port of the steering gear 6 and an R2 port of the flow control valve 8 are connected in parallel and simultaneously connected with an R1 port of the flow amplification valve; in the manual mode, the flow control valve 8 is not powered, at the moment, the steering wheel is operated to open the steering gear, and the L, R port of the steering gear outputs flow related to the rotating speed of the steering wheel to the control cavity of the flow amplification valve to generate pressure difference so as to change the direction of the flow amplification valve; when the steering gear 6 works, the neutral position of the flow control valve 8 is cut off, and the L, R port of the steering gear 6 acts on the L1 port and the R1 port of the flow amplification valve 8 respectively to control steering; in the electric control mode, the flow control valve 8 is electrified, when the flow control valve 8 works, the middle position of the steering gear 6 is cut off, and the ports L2 and R2 of the flow control valve 8 respectively act on the ports L1 and R1 of the flow amplification valve 8 to control steering, so that the electric control of the steering gear is realized.
The pilot oil source valve 5 determines the oil supply pressure of the pilot valve 4 and the electric proportional pressure reducing valve 7, the pilot valve 4 and the electric proportional pressure reducing valve 7 are connected in series to jointly control the multi-way valve to change direction to realize the whole machine working device, and the whole machine working device specifically comprises: the port a1 of the pilot valve 4 is connected with the port a1P of the electro proportional pressure reducing valve 7, the port a2 of the pilot valve 4 is connected with the port a2P of the electro proportional pressure reducing valve 7, the port b1 of the pilot valve 4 is connected with the port b1P of the electro proportional pressure reducing valve 7, the port b2 of the pilot valve 4 is connected with the port b2P of the electro proportional pressure reducing valve 7, the corresponding port a1T of the electro proportional pressure reducing valve 7 is connected with the port a1 of the multi-way valve 2, the port a2T of the electro proportional pressure reducing valve 7 is connected with the port a2 of the multi-way valve 2, the port b1T of the electro proportional pressure reducing valve 7 is connected with the port b1 of the multi-way valve 2, and the port b2T of the electro proportional pressure reducing valve 7 is connected with the port b2 of the multi-way valve 2; in the manual mode, the electric proportional pressure reducing valve 7 is not electrified, when the pilot valve 4 works, the electric proportional pressure reducing valve 7 does not work, and at the moment, all the ports P of the electric proportional pressure reducing valve 7 are communicated with the port T, namely, the port a1P is communicated with the port a1T, the port a2P is communicated with the port a2T, the port b1P is communicated with the port b1T, and the port b2P is communicated with the port b 2T; the pilot valve 4 is connected with the electric proportional pressure reducing valve 7 in series, the multi-way valve 2 is controlled by the pilot valve 4, and the pressure of each output port of the pilot valve 4 acts on each pilot port of the multi-way valve 2 to realize the action of the working device. Under the electric control mode, the electric proportional pressure reducing valve 7 is electrified, when the electric proportional pressure reducing valve 7 works, the pilot valve 4 does not work, the pilot valve 4 is cut off, the multi-way valve 2 is controlled by the electric proportional pressure reducing valve 7, and the pressure of each output port of the electric proportional pressure reducing valve 7 acts on each pilot port of the multi-way valve 2 to realize the action of a working device, so that the electric control of the multi-way valve is realized.
The flow control valve 8 comprises an electro-proportional valve 11 and a pressure compensator 12, an oil inlet of the electro-proportional valve 11 is communicated with a control cavity of the pressure compensator 12, and an oil outlet of the electro-proportional valve 11 is connected with a spring cavity of the pressure compensator 12.
The flow control valve 8 can realize proportional output flow, specifically, by controlling the opening of the electro proportional valve 11, the pilot oil generates a pressure drop Δ p through the electro proportional valve 11 to act on two ends of the pressure compensator 12, i.e., inlet pressure acts on the non-spring cavity and outlet pressure acts on the spring cavity. When the flow control valve 8 is not electrified, no flow passes through the flow control valve 8, and all pilot oil is supplied to the steering gear 6 and the pilot oil source valve 5; when the vehicle turns to the right, the electro-proportional valve 11 is powered on and opened, hydraulic oil from the gear pump 1 passes through the electro-proportional valve 11 to enable an oil inlet and an oil outlet of the electro-proportional valve 11 to generate differential pressure to act on two ends of the pressure compensator 12 respectively, and at the moment, the output flow is as follows:
wherein q is the flow passing through the electric proportional valve; cdIs a flow coefficient, is a constant; a. theTIs the opening area of the electro proportional valve; delta p is the pressure difference of an oil inlet and an oil outlet of the electro proportional valve; rho is the hydraulic oil density; Δ p is related to the pressure compensator spring force, CdAnd ρ is a constant, the flow rate control valve can output a flow rate irrespective of the pressure.
Since the spool direction change of the flow rate amplification valve 3 is flow rate dependent, the pilot control of the flow rate amplification valve 3 needs to output a stable flow rate independent of the pressure to ensure the control performance of the steering.
The flow control valve 8 also comprises a three-position four-way electromagnetic directional valve 13, when the steering is right, an L2 port of the flow control valve 8 is electrified, at the moment, an oil inlet is arranged at a P port of the three-position four-way electromagnetic directional valve 13, the oil at the A port returns through a flow amplifying valve control cavity and a B port after the oil at the A port is discharged, and the pilot oil generates a pressure difference through a pilot port of the flow amplifying valve 3 to control the reversing of the valve core; when the vehicle turns left, the R2 port of the flow control valve 8 is electrified, at the moment, oil enters the P port of the three-position four-way electromagnetic directional valve 13, oil flows out of the B port and returns through the control cavity of the flow amplifying valve through the A port, and pilot oil generates pressure difference through the pilot port of the flow amplifying valve 3 to control the reversing of the valve core.
In the embodiment, a set of electric control device is connected in parallel with the existing hydraulic device, and the loader is controlled by the hydraulic device in a manual mode; under the electric control mode, the loader is controlled by the electric control device and the hydraulic device together, so that the control of each action program of the whole machine is realized, the electric control can be realized under the condition of not changing the integral structure of the existing hydraulic device, and the remote control and the unmanned performance of the loader can be simultaneously met; all the improved parts are made in a domestic manner, so that the manufacturing cost is reduced, and the dependence on an inlet part is eliminated.
Example two:
based on the electrically controlled hydraulic system of the loader according to the first embodiment, the present embodiment provides a loader, and the loader is configured with the electrically controlled hydraulic system of the loader according to the first embodiment.
The above description is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, several modifications and variations can be made without departing from the technical principle of the present invention, and these modifications and variations should also be regarded as the protection scope of the present invention.
Claims (10)
1. An electric control hydraulic system of a loader is characterized by comprising a hydraulic device and an electric control device, wherein the electric control device is connected with the hydraulic device in parallel; in the manual mode, the loader is controlled by the hydraulic device; in the electric control mode, the loader is controlled by the electric control device and the hydraulic device together.
2. The electrically controlled hydraulic system of the loader according to claim 1, characterized in that the hydraulic device comprises a gear pump (1), a multi-way valve (2), a flow amplifying valve (3), a pilot valve (4), a pilot oil source valve (5) and a diverter (6), and the electrically controlled device comprises an electric proportional pressure reducing valve (7) and a flow control valve (8);
the oil outlet of the gear pump (1) is respectively communicated with the oil inlets of the multi-way valve (2), the flow amplifying valve (3), the pilot oil source valve (5), the steering gear (6) and the flow control valve (8);
the oil outlet of the pilot oil source valve (5) is respectively communicated with the oil inlets of the pilot valve (4) and the electric proportional pressure reducing valve (7), and is communicated with the multi-way valve (2) through the pilot valve (4) and the electric proportional pressure reducing valve (7);
the diverter (6) is connected with the flow control valve (8) in parallel and then is communicated with the flow amplification valve (3).
3. The electrically controlled hydraulic system of a loader as claimed in claim 2 wherein the port a1P of the electro proportional pressure reducing valve (7) communicates with the port a1 of the pilot valve (4), the port a1T of the electro proportional pressure reducing valve (7) communicates with the port a1 of the multi-way valve (2);
the port a2P of the electro-proportional pressure reducing valve (7) is communicated with the port a2 of the pilot valve (4), and the port a2T of the electro-proportional pressure reducing valve (7) is communicated with the port a2 of the multi-way valve (2);
the port b1P of the electro-proportional pressure reducing valve (7) is communicated with the port b1 of the pilot valve (4), and the port b1T of the electro-proportional pressure reducing valve (7) is communicated with the port b1 of the multi-way valve (2);
the port b2P of the electro-proportional pressure reducing valve (7) is communicated with the port b2 of the pilot valve (4), and the port b2T of the electro-proportional pressure reducing valve (7) is communicated with the port b2 of the multi-way valve (2);
in a manual mode, the electric proportional pressure reducing valve (7) cannot be electrified, a port a1P is communicated with a port a1T, a port a2P is communicated with a port a2T, a port b1P is communicated with a port b1T, a port b2P is communicated with a port b2T, the pilot valve (4) is connected with the electric proportional pressure reducing valve (7) in series, and the multi-way valve (2) is controlled by the pilot valve (4);
in the electric control mode, the electric proportional pressure reducing valve (7) is electrified, the pilot valve (4) is cut off, and the multi-way valve (2) is controlled by the electric proportional pressure reducing valve (7).
4. An electrically controlled hydraulic system for a loader as claimed in claim 2 wherein the port R1 of the flow amplification valve (3) communicates with the port R of the steering gear (6) and the port R2 of the flow control valve (8), respectively; an L1 port of the flow amplification valve (3) is respectively communicated with an L port of the steering gear (6) and an L2 port of the flow control valve (8); in the manual mode, the flow control valve (8) is not electrified, and the steering gear (6) controls steering; in the electric control mode, the flow control valve (8) is electrified and controls steering.
5. The electrically controlled hydraulic system of a loader as claimed in claim 2 wherein the flow control valve (8) comprises an electro-proportional valve (11) and a pressure compensator (12), the oil inlet of the electro-proportional valve (11) is communicated with the control chamber of the pressure compensator (12), and the oil outlet of the electro-proportional valve (11) is connected with the spring chamber of the pressure compensator (12).
6. An electrically controlled hydraulic system according to claim 5, characterized in that when the flow control valve (8) is not energized, no flow passes through the flow control valve (8), and all the pilot oil is supplied to the steering gear (6) and the pilot oil source valve (5); when the steering wheel turns to the right, the electric proportional valve (11) is electrified to be opened, hydraulic oil discharged from the gear pump (1) passes through the electric proportional valve (11) to enable the oil inlet and the oil outlet of the electric proportional valve (11) to generate differential pressure to act on two ends of the pressure compensator (12) respectively, and at the moment, the output flow is as follows:
wherein q is the flow passing through the electric proportional valve; cdIs a flow coefficient, is a constant; a. theTIs the opening area of the electro proportional valve; delta p is the pressure difference of an oil inlet and an oil outlet of the electro proportional valve; ρ is the hydraulic oil density.
7. The electrically controlled hydraulic system of the loader as claimed in claim 6, wherein the flow control valve (8) further comprises a three-position four-way electromagnetic directional valve (13), when the steering wheel is turned to the right, the port L2 of the flow control valve (8) is powered, the port P of the three-position four-way electromagnetic directional valve (13) is powered, and the oil is fed into the port A and then returned to the port B through the control cavity of the flow amplifying valve; when the vehicle turns left, the R2 port of the flow control valve (8) is electrified, at the moment, the P port of the three-position four-way electromagnetic directional valve (13) enters oil, and the oil from the B port returns through the A port by the control cavity of the flow amplifying valve.
8. An electrically controlled hydraulic system for a loader according to claim 1 further comprising a switch valve for switching between the manual mode and the electrical control mode.
9. The electrically controlled hydraulic system of the loader as claimed in claim 1, wherein the gear pump (1) comprises a pilot pump, a steering pump and a working pump, and the oil outlet of the pilot pump is respectively communicated with the oil inlets of the pilot oil source valve (5), the steering gear (6) and the flow control valve (8); an oil outlet of the steering pump is communicated with an oil inlet of the flow amplification valve (3); and an oil outlet of the working pump is respectively communicated with a PF port of the flow amplification valve (3) and an oil inlet of the multi-way valve (2).
10. A loader configured with an electrically controlled hydraulic system of a loader according to any one of claims 1 to 9.
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| CN202111068003.5A CN113757203B (en) | 2021-09-13 | 2021-09-13 | Loader electric control hydraulic system and loader |
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| CN202111068003.5A CN113757203B (en) | 2021-09-13 | 2021-09-13 | Loader electric control hydraulic system and loader |
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| CN213862400U (en) * | 2020-12-25 | 2021-08-03 | 雷沃工程机械集团有限公司 | Hydraulic system for realizing electric control of steering system of loader |
| CN214061766U (en) * | 2020-12-15 | 2021-08-27 | 雷沃工程机械集团有限公司 | Hydraulic system for realizing electric control of loader work |
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| EP0352654A2 (en) * | 1988-07-27 | 1990-01-31 | Clark Equipment Company | Electrically controlled auxiliary hydraulic system for a skid steer loader |
| GB2315102A (en) * | 1996-07-10 | 1998-01-21 | Samsung Heavy Ind | Hydraulic system for power loaders |
| CN203670337U (en) * | 2013-12-19 | 2014-06-25 | 杭叉集团股份有限公司 | Load-sensitive electric proportional multi-way valve |
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| CN204985186U (en) * | 2015-08-26 | 2016-01-20 | 徐工集团工程机械股份有限公司科技分公司 | Automatically controlled switching core hydraulic system and engineering machinery |
| CN105350598A (en) * | 2015-10-21 | 2016-02-24 | 徐工集团工程机械股份有限公司科技分公司 | Hydraulic control system for improving energy saving performance of loader and control method of hydraulic control system |
| CN106321541A (en) * | 2016-08-30 | 2017-01-11 | 中煤科工集团西安研究院有限公司 | Electric-hydraulic double-control hydraulic system and method for vehicle-mounted drilling machine |
| CN207685902U (en) * | 2017-04-27 | 2018-08-03 | 广西柳工机械股份有限公司 | The loading machine pilot control fuel feeding energy and electric power storage device for supplying |
| CN109083223A (en) * | 2018-07-27 | 2018-12-25 | 山东临工工程机械有限公司 | The hydraulic system of remote control loading machine |
| CN214061766U (en) * | 2020-12-15 | 2021-08-27 | 雷沃工程机械集团有限公司 | Hydraulic system for realizing electric control of loader work |
| CN213862400U (en) * | 2020-12-25 | 2021-08-03 | 雷沃工程机械集团有限公司 | Hydraulic system for realizing electric control of steering system of loader |
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| CN113757203B (en) | 2022-04-15 |
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Denomination of invention: A loader electromechanical control hydraulic system and loader Effective date of registration: 20221228 Granted publication date: 20220415 Pledgee: Xugong Group Finance Co.,Ltd. Pledgor: XCMG CONSTRUCTION MACHINERY Co.,Ltd. SCIENCE AND TECHNOLOGY BRANCH Registration number: Y2022320000796 |