CN114658708A - Load rotating speed double-sensitive anti-flow saturation system and engineering mechanical device thereof - Google Patents
Load rotating speed double-sensitive anti-flow saturation system and engineering mechanical device thereof Download PDFInfo
- Publication number
- CN114658708A CN114658708A CN202210372706.5A CN202210372706A CN114658708A CN 114658708 A CN114658708 A CN 114658708A CN 202210372706 A CN202210372706 A CN 202210372706A CN 114658708 A CN114658708 A CN 114658708A
- Authority
- CN
- China
- Prior art keywords
- valve
- interface
- way reversing
- reversing valve
- load
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 230000007246 mechanism Effects 0.000 claims abstract description 77
- 239000010720 hydraulic oil Substances 0.000 claims abstract description 47
- 239000003921 oil Substances 0.000 claims abstract description 38
- 238000006073 displacement reaction Methods 0.000 claims description 28
- 230000009977 dual effect Effects 0.000 claims description 4
- 238000000034 method Methods 0.000 description 10
- 230000008569 process Effects 0.000 description 10
- 230000000875 corresponding effect Effects 0.000 description 7
- 230000009471 action Effects 0.000 description 6
- 230000008878 coupling Effects 0.000 description 4
- 238000010168 coupling process Methods 0.000 description 4
- 238000005859 coupling reaction Methods 0.000 description 4
- 238000001914 filtration Methods 0.000 description 4
- 230000008859 change Effects 0.000 description 3
- 230000001276 controlling effect Effects 0.000 description 3
- 230000007547 defect Effects 0.000 description 3
- 230000001105 regulatory effect Effects 0.000 description 3
- 230000008901 benefit Effects 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 2
- 230000002079 cooperative effect Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000013016 damping Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 230000008676 import Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 230000007935 neutral effect Effects 0.000 description 1
- 229920006395 saturated elastomer Polymers 0.000 description 1
Images
Classifications
-
- 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
-
- 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
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
-
- 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
- F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
- F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
-
- 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
- F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention provides a load rotating speed double-sensitive anti-flow saturation system and an engineering mechanical device thereof, which comprise an operation assembly, a main pump source, a pilot control pump source, a load sensitive mechanism and a hydraulic oil tank, wherein the operation assembly comprises a main pump source, a pilot control pump source, a load sensitive mechanism and a hydraulic oil tank; the main pump source and the pilot control pump source are connected with a hydraulic oil tank; the main pump source is connected with the load sensing mechanism; the pilot control pump source is connected with the load sensitive mechanism and the main pump source; the load sensitive mechanism is used for connecting a plurality of executing devices; the pilot control pump source is used for adjusting the pressure difference between the input end and the output end of the load sensitive mechanism when the main pump source receives the accelerator signal transmitted by the operating assembly; and the load sensitive mechanism is configured to adjust the system to enter a saturation region when the handle signal transmitted by the operating assembly is higher than a preset value, and oil is supplied to each execution device according to the handle signal input proportion. In addition, the differential pressure value of the traditional load-sensitive system is constant, the given differential pressure value cannot be well adapted to different operation requirements, and when the flow supply of the hydraulic pump of the system is insufficient, hydraulic oil cannot flow into each actuator according to the input proportion.
Description
Technical Field
The invention relates to the technical field of hydraulic transmission, in particular to a load rotating speed double-sensitive anti-flow saturation system and an engineering mechanical device thereof.
Background
The engineering machinery is widely applied to various earthwork construction fields and is one of the important strut industries in China, but the traditional engineering machinery has the defects of limited flow pressure matching characteristic, poor controllability and the like. Typical hydraulic systems of engineering machinery in the current market can be divided into negative flow, positive flow, load sensitive mechanisms and the like mainly according to different flow matching modes; the negative flow system is based on an open center oil way, detects return oil pressure through a middle way return orifice and feeds the return oil pressure back to a hydraulic pump displacement adjusting mechanism to perform variable pump displacement control to realize flow matching, but the system has the problems that the displacement adjustment is always lagged behind the system load change, and the controllability of each actuator is greatly influenced by the load; the positive flow system is also based on an open center oil way, the flow matching of the pump and the load is realized by directly changing the displacement of the pump and the opening degree of the proportional reversing valve through the pilot handle, and compared with a negative flow system, the positive flow system has the advantage that the displacement adjustment can be controlled in real time according to the load requirement, but the problem that the controllability of each actuator is greatly influenced by the load exists; the load sensitive system is based on a closed center oil way, the maximum load pressure is detected and fed back to control the displacement of the hydraulic pump, so that the outlet pressure of the hydraulic pump is only higher than the maximum load pressure value by a fixed value, the pressure difference of each throttle valve port is maintained to be a preset value through a pressure compensation valve, the through flow of the throttle valve is only related to the opening area of the throttle valve and is not related to the load, and the controllability is improved; when the flow supply of the hydraulic pump is insufficient, the flow supply of the system is insufficient, the valve port pressure difference can drop, the valve port pressure difference of the reversing valve of each actuator can be different, and hydraulic oil can still not flow into each actuator according to the input control proportion.
In view of this, the present application is presented.
Disclosure of Invention
The invention discloses a load rotating speed double-sensitive anti-flow saturation system and an engineering mechanical device thereof, aiming at solving the problems that the pressure difference value of the traditional load sensitive system is the set value of a system spring, the pressure difference is constant in the working process, and the given pressure difference value still cannot be well adapted to different operation requirements under different working conditions; and when the flow supply of the hydraulic pump is insufficient, the flow supply of the system is insufficient, the valve port pressure difference can drop, the valve port pressure difference of the reversing valve of each actuator can be distinguished, and hydraulic oil can still not flow into each actuator according to the input control proportion.
The invention provides a load rotating speed double-sensitive anti-flow saturation system, which comprises an operation component, a main pump source, a pilot control pump source, a load sensitive mechanism and a hydraulic oil tank, wherein the operation component is connected with the main pump source through a pipeline;
the input end of the main pump source and the input end of the pilot control pump source are connected with the hydraulic oil tank;
the output end of the main pump source is connected with the input end of the load sensitive mechanism;
the output end of the pilot control pump source is connected with the control end of the load sensitive mechanism and the control end of the main pump source;
the output end of the load sensitive mechanism is connected with the control end of the pilot control pump source and the control end of the main pump source;
the output end of the load sensitive mechanism is used for connecting a plurality of executing devices;
the pilot control pump source is used for adjusting the pressure difference between the input end and the output end of the load sensitive mechanism when the main pump source receives an accelerator signal transmitted by the operating assembly;
and the load sensitive mechanism is configured to adjust the system to enter a saturation region when the handle signal transmitted by the operating assembly is higher than a preset value, and supply oil to each execution device according to the input proportion of the handle signal.
Preferably, the operating assembly comprises an operating handle and a throttle knob, an output end of the operating handle is electrically connected with an input end of the load sensitive mechanism, and an output end of the throttle knob is electrically connected with an input end of the main pump source.
Preferably, the main pump source comprises a power source, a main pump, a first two-position three-way reversing valve, a first displacement adjusting mechanism and a second displacement adjusting mechanism;
the power source is mechanically connected with the main pump, the main pump is mechanically connected with the pilot control pump source, the load sensitive mechanism and the hydraulic oil tank pipeline, the inlet of the main pump is connected with the hydraulic oil tank pipeline, the outlet of the main pump is connected with the control port pipeline of the first displacement adjusting mechanism, the first interface of the first two-position three-way reversing valve is connected with the second displacement adjusting mechanism pipeline, the second interface of the first two-position three-way reversing valve is connected with the hydraulic oil tank pipeline, and the first two-position three-way reversing valve is connected with the load sensitive mechanism pipeline.
Preferably, the pilot control pump source comprises a pilot pump and a rotating speed sensitive valve;
the inlet of the pilot pump is connected with the hydraulic oil tank through a pipeline, the outlet of the pilot pump is connected with an interface pipeline of the rotating speed sensitive valve, the input end of the rotating speed sensitive valve is connected with the hydraulic oil tank through a pipeline, and the interface of the rotating speed sensitive valve is connected with the interface of the first two-position three-way reversing valve and the input end pipeline of the load sensitive mechanism.
Preferably, the rotating speed sensitive valve comprises a first two-position two-way reversing valve and a second two-position three-way reversing valve;
the outlet of the pilot pump is in pipeline connection with a first interface of the first two-position two-way reversing valve, a left side control cavity of the first two-position two-way reversing valve and a lower side control cavity of the second two-position three-way reversing valve, a second interface of the first two-position two-way reversing valve is in pipeline connection with a second interface of the second two-position three-way reversing valve, an upper side control cavity of the second two-position three-way reversing valve and a right side control cavity of the first two-position two-way reversing valve, a third interface of the second two-position three-way reversing valve is in pipeline connection with the hydraulic oil tank, a second interface of the first two-position two-way reversing valve is in pipeline connection with a third interface of the first two-position three-way reversing valve and an input end of the load sensitive mechanism, and a first interface of the second two-position three-way reversing valve is in pipeline connection with an upper control cavity of the second two-position three-way reversing valve and an input end of the load sensitive mechanism, And the lower side control cavity pipeline of the first two-position three-way reversing valve is connected.
Preferably, the load-sensitive mechanism comprises a proportional directional control valve, a first pressure compensation valve, a second pressure compensation valve, an actuator, a shuttle valve, a second two-position two-way directional control valve, a differential pressure reducing valve and a throttling hole;
wherein, the input end of the proportional reversing valve is connected with the hydraulic oil tank pipeline, the interface of the proportional reversing valve is connected with the interface of the first pressure compensation valve, the interface of the second pressure compensation valve, the interface of the actuator and the interface of the shuttle valve, the second interface of the first pressure compensation valve and the second interface of the second pressure compensation valve are connected with the interface pipeline of the actuator, the third interface of the shuttle valve is connected with the right control cavity of the first pressure compensation valve, the right control cavity of the second pressure compensation valve, the first interface of the throttling hole and the left control cavity of the second two-position two-way reversing valve through pipelines, the lower control cavity of the differential pressure reducing valve is connected with the second interface of the throttling hole and the first interface pipeline of the differential pressure reducing valve through pipelines, and the second interface of the differential pressure reducing valve is connected with the hydraulic oil tank pipeline, the second interface of the second two-position two-way reversing valve is connected with the hydraulic oil tank pipeline, the main pump is connected with the first interface of the second two-position two-way reversing valve, the right control cavity of the second two-position two-way reversing valve and the upper side control cavity of the differential pressure reducing valve through pipelines, the third interface of the differential pressure reducing valve is connected with the second interface of the first two-position two-way reversing valve through pipelines, the left control cavity of the second two-position two-way reversing valve is connected with the first interface of the second two-position three-way reversing valve through pipelines, and the first interface of the differential pressure reducing valve is connected with the upper control cavity of the first two-position three-way reversing valve through pipelines.
Preferably, the proportional reversing valve comprises a first three-position five-way reversing valve and a second three-position five-way reversing valve;
wherein a first interface of the first three-position five-way reversing valve is connected with a first interface of the second three-position five-way reversing valve and the hydraulic oil tank pipeline, a second interface of the first three-position five-way reversing valve is connected with a first interface of the first pressure compensation valve and a left side control cavity pipeline of the first pressure compensation valve, a third interface of the first three-position five-way reversing valve is connected with an interface of the actuator, a fourth interface of the first three-position five-way reversing valve is connected with the first interface pipeline of the shuttle valve, a second interface of the second three-position five-way reversing valve is connected with the first interface of the second pressure compensation valve and the left side control cavity pipeline of the second pressure compensation valve, a third interface of the second three-position five-way reversing valve is connected with the interface pipeline of the actuator, and a fourth interface of the second three-position five-way reversing valve is connected with the second interface pipeline of the shuttle valve, the main pump is connected with a fifth interface of the first three-position five-way reversing valve and a fifth interface of the second three-position five-way reversing valve through pipelines.
Preferably, the actuator comprises a first execution oil cylinder and a second execution oil cylinder;
the third interface of the first three-position five-way reversing valve is connected with the first interface pipeline of the first execution oil cylinder, the second interface of the first pressure compensation valve is connected with the second interface pipeline of the first execution oil cylinder, the third interface of the second three-position five-way reversing valve is connected with the first interface pipeline of the second execution oil cylinder, and the second interface of the second pressure compensation valve is connected with the second interface pipeline of the second execution oil cylinder.
The second embodiment of the invention provides a load rotating speed double-sensitive anti-flow saturation engineering mechanical device which comprises the load rotating speed double-sensitive anti-flow saturation system.
In summary, according to the load-rotation-speed dual-sensing anti-flow saturation system and the engineering mechanical device thereof provided by this embodiment, the flow matching of the hydraulic pump is realized by detecting the maximum load pressure, the difference between the outlet pressure of the hydraulic pump and the maximum load pressure is controlled to be a certain control value, the rotation speed of the power source is monitored by the rotation speed sensitive valve, and the target control pressure difference of the pressure compensation valve of the load-sensitive mechanism is adjusted by the rotation speed sensitive valve, so as to realize the valve core-flow corresponding relation of the main valve under different pressure differences, thereby solving the problem that the pressure difference value of the conventional load-sensitive system is the set value of the system spring, and the pressure difference is constant during the working process, and the given pressure difference value still cannot be well adapted to different working requirements under different working conditions; and when the flow supply of the hydraulic pump is insufficient, the flow supply of the system is insufficient, the valve port pressure difference can drop, the valve port pressure difference of the reversing valve of each actuator can be distinguished, and hydraulic oil can still not flow into each actuator according to the input control proportion.
Drawings
Fig. 1 is a schematic structural diagram of a load rotation speed dual-sensitive anti-flow saturation system provided by the invention.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present invention more apparent, the technical solutions of the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings of the embodiments of the present invention, and it is obvious that the described embodiments are some, but not all embodiments of the present invention. All other embodiments, which can be obtained by a person skilled in the art without any inventive step based on the embodiments of the present invention, are within the scope of the present invention. Thus, the following detailed description of the embodiments of the present invention, presented in the figures, is not intended to limit the scope of the invention, as claimed, but is merely representative of selected embodiments of the invention. All other embodiments, which can be obtained by a person skilled in the art without any inventive step based on the embodiments of the present invention, are within the scope of the present invention.
The following detailed description of specific embodiments of the invention refers to the accompanying drawings.
The invention discloses a load rotating speed double-sensitive anti-flow saturation system and an engineering mechanical device thereof, aiming at solving the problems that the pressure difference value of a traditional load sensitive mechanism is a system spring set value, the pressure difference is constant in the working process, and the given pressure difference value still cannot be well adapted to different operation requirements under different working conditions; and when the flow supply of the hydraulic pump is insufficient, the flow supply of the system is insufficient, the valve port pressure difference can drop, the valve port pressure difference of the reversing valve of each actuator can be distinguished, and hydraulic oil can still not flow into each actuator according to the input control proportion.
Referring to fig. 1, a first embodiment of the present invention provides a load rotation speed dual-sensitive anti-flow saturation system, which includes an operation component, a main pump source, a pilot control pump source, a load sensitive mechanism, and a hydraulic oil tank 19;
the input end of the main pump source and the input end of the pilot control pump source are connected with the hydraulic oil tank 19;
the output end of the main pump source is connected with the input end of the load sensitive mechanism;
the output end of the pilot control pump source is connected with the control end of the load sensitive mechanism and the control end of the main pump source;
the output end of the load sensitive mechanism is connected with the control end of the pilot control pump source and the control end of the main pump source;
the output end of the load sensitive mechanism is used for connecting a plurality of executing devices;
the pilot control pump source is used for adjusting the pressure difference between the input end and the output end of the load sensitive mechanism when the main pump source receives an accelerator signal transmitted by the operating assembly;
and the load sensitive mechanism is configured to adjust the system to enter a saturation region when the handle signal transmitted by the operating assembly is higher than a preset value, and supply oil to each execution device according to the input proportion of the handle signal.
Preferably, the operating assembly comprises an operating handle and a throttle knob, an output end of the operating handle is electrically connected with an input end of the load sensitive mechanism, and an output end of the throttle knob is electrically connected with an input end of the main pump source.
Preferably, the main pump source comprises a power source 1, a main pump 2, a first two-position three-way reversing valve 6, a first displacement adjusting mechanism 4 and a second displacement adjusting mechanism 5;
wherein, power supply 1 with 2 mechanical connections of main pump, main pump 2 with the pilot control pump source the sensitive mechanism of load the 19 pressure connections of hydraulic tank, the import of main pump 2 with 19 tube couplings of hydraulic tank, the export of main pump 2 with the control mouth tube coupling of first displacement adjustment mechanism 4, the first interface P of first two-position three-way switching-over valve 6 with 5 tube couplings of second displacement adjustment mechanism, the second interface B of first two-position three-way switching-over valve 6 with 19 pressure connections of hydraulic tank liquid, first two-position three-way switching-over valve 6 with the sensitive mechanism tube coupling of load.
Preferably, the pilot-controlled pump source comprises a pilot pump 3 and a rotation speed sensitive valve;
the inlet of the pilot pump 3 is connected with the hydraulic oil tank 19 through a pipeline, the outlet of the pilot pump 3 is connected with the interface pipeline of the rotating speed sensitive valve, the input end of the rotating speed sensitive valve is connected with the hydraulic oil tank 19 through a pipeline, and the interface of the rotating speed sensitive valve is connected with the interface of the first two-position three-way reversing valve 6 and the input end pipeline of the load sensitive mechanism.
Preferably, the rotating speed sensitive valve comprises a first two-position two-way reversing valve 7 and a second two-position three-way reversing valve 8;
wherein, the outlet of the pilot pump 3 is connected with the first interface P of the first two-position two-way reversing valve 7, the left control cavity of the first two-position two-way reversing valve 7 and the lower control cavity of the second two-position three-way reversing valve 8 through pipelines, the second interface T of the first two-position two-way reversing valve 7 is connected with the 8 second interface B of the second two-position three-way reversing valve, the upper control cavity of the second two-position three-way reversing valve 8 and the right control cavity of the first two-position three-way reversing valve 7 through pipelines, the third interface A of the second two-position three-way reversing valve 8 is connected with the hydraulic oil tank 19 through pipelines, the second interface T of the first two-position two-way reversing valve 7 is connected with the third interface A of the first two-position three-way reversing valve 6 and the input end pipeline of the load sensitive mechanism, the first interface P of the second two-position three-way reversing valve 8 is connected with the upper control cavity of the second two-position three-way reversing valve 8 through pipelines, The input end of the load sensing mechanism is connected with the control cavity pipeline at the lower side of the first two-position three-way reversing valve 6.
Preferably, the load-sensitive mechanism comprises a proportional directional control valve, a first pressure compensation valve 11, a second pressure compensation valve 12, an actuator, a shuttle valve 15, a second two-position two-way directional control valve 17, a differential pressure reducing valve 16 and an orifice 18;
wherein, the input end of the proportional directional valve is connected with the hydraulic oil tank 19 by a pipeline, the interface of the proportional directional valve is connected with the interface of the first pressure compensation valve 11, the interface of the second pressure compensation valve 12, the interface of the actuator and the interface of the shuttle valve 15 by pipelines, the second interface T of the first pressure compensation valve 11 and the second interface T of the second pressure compensation valve 12 are connected with the interface of the actuator by pipelines, the third interface C of the shuttle valve 15 is connected with the right control cavity of the first pressure compensation valve 11, the right control cavity of the second pressure compensation valve 12, the first interface a of the orifice 18 and the left control cavity of the second two-position two-way directional valve 7 by pipelines, the lower control cavity of the differential pressure reducing valve 16 is connected with the second interface B of the orifice 18 and the first interface a of the differential pressure reducing valve 16 by pipelines, the second interface T of the differential pressure reducing valve 16 is connected with the hydraulic oil tank 19 through a pipeline, the second interface T of the second two-position two-way reversing valve 17 is connected with the hydraulic oil tank 19 through a pipeline, the main pump 2 is connected with the first interface P of the second two-position two-way reversing valve 17, the right side control cavity of the second two-position two-way reversing valve 17 and the upper side control cavity of the differential pressure reducing valve 16 through a pipeline, the third interface P of the differential pressure reducing valve 16 is connected with the second interface T of the first two-position two-way reversing valve 7 through a pipeline, the left side control cavity of the second two-position two-way reversing valve 16 is connected with the first interface P of the second two-position three-way reversing valve 8 through a pipeline, and the first interface A of the differential pressure reducing valve 16 is connected with the upper control cavity of the first two-position three-way reversing valve 6 through a pipeline.
Preferably, the proportional directional control valve comprises a first three-position five-way directional control valve 9 and a second three-position five-way directional control valve 10;
wherein, the first port T of the first three-position five-way reversing valve 9 is connected with the first port T of the second three-position five-way reversing valve 10 and the hydraulic oil tank 19 through pipelines, the second port a of the first three-position five-way reversing valve 9 is connected with the first port P of the first pressure compensating valve 11 and the left side control cavity pipeline of the first pressure compensating valve 11, the third port B of the first three-position five-way reversing valve 9 is connected with the port of the actuator, the fourth port C of the first three-position five-way reversing valve 9 is connected with the first port a of the shuttle valve 15 through pipelines, the second port a of the second three-position five-way reversing valve 10 is connected with the first port P of the second pressure compensating valve 12 and the left side control cavity pipeline of the second pressure compensating valve 12, and the third port B of the second three-position five-way reversing valve 10 is connected with the port pipeline of the actuator, the fourth port C of the second three-position five-way reversing valve 10 is connected with the second port B of the shuttle valve 15 through a pipeline, and the main pump 2 is connected with the fifth port P of the first three-position five-way reversing valve 9 and the fifth port P of the second three-position five-way reversing valve 10 through a pipeline.
Preferably, the actuator comprises a first execution oil cylinder 13 and a second execution oil cylinder 14;
the third port B of the first three-position five-way reversing valve 9 is connected with the first port B of the first execution cylinder 13 through a pipeline, the second port T of the first pressure compensation valve 11 is connected with the second port a of the first execution cylinder 13 through a pipeline, the third port B of the second three-position five-way reversing valve 10 is connected with the first port B of the second execution cylinder 14 through a pipeline, and the second port T of the second pressure compensation valve 12 is connected with the second port a of the second execution cylinder 14 through a pipeline.
Specifically, in this embodiment, aiming at the defects of the hydraulic transmission of the existing engineering machinery, especially the defects of the traditional load-sensitive system, the load-rotating-speed dual-sensitive flow-resistant saturation system monitors the rotating speed of the power source by using the rotating speed-sensitive valve, and adjusts the target control differential pressure of the pressure compensation valve of the load-sensitive mechanism by using the rotating speed-sensitive valve, so as to realize the valve core-flow corresponding relation of the main valve under different differential pressures, and improve the control characteristics of different operation processes such as fine operation and large-flow operation; meanwhile, a differential pressure reducing valve is introduced into the load sensitive mechanism, dynamic analog filtering is carried out on the differential pressure between the outlet pressure of the pump and the maximum load pressure, and the analog signal is used for displacement control of the pump and target compensation differential pressure control of a pressure compensation valve in a main control valve, so that the system has higher stability. In addition, the load difference is compensated through the pressure compensation valve at the rear side of the main control valve, the main control valve pressure difference of different actuators is kept to be customized, the main control valve pressure difference of different actuators is the same, the linear control degree of a system pilot input signal and the actuator target control speed is improved, and the coordination control performance of the multiple actuators in the rapid movement process is ensured.
In this embodiment, the flow matching of the hydraulic pump is realized by detecting the maximum load pressure, the difference between the outlet pressure of the hydraulic pump and the maximum load pressure is controlled to be a certain control value, the control value is controlled by a rotation speed sensitive valve based on the rotation speed of the power source 1, and under the condition that the power source 1 runs at a low speed, the target control differential pressure between the outlet pressure of the hydraulic pump and the maximum load pressure is reduced, so that the differential pressure of the throttle orifice of the proportional directional valve is reduced, and the control precision of the pilot signal to the target flow is improved. Under the condition that the power source 1 runs at a high speed, the target control pressure difference between the outlet pressure of the hydraulic pump and the maximum load pressure is increased, so that the pressure difference of the throttling port of the proportional directional valve is increased, the through-flow capacity of the unit opening degree of the throttling port is improved, and the action speed of the system is further improved. In addition, the system adopts a compensation mode after the valve to reduce the influence of load change on the system controllability, and when the multiple actuators operate at high speed, the pump source cannot simultaneously meet the oil supply flow rate of the multiple actuators during quick action, and the hydraulic system can still distribute the flow rate of each actuator in equal proportion according to handle input signals, so that the controllability of the cooperative action of the multiple actuators is ensured.
The specific working principle of the invention is as follows:
the load rotating speed double-sensitive anti-flow saturation system regulates and controls the pressure difference between the input end and the output end of the proportional reversing valve by controlling the accelerator knob, and regulates and controls the opening degree of a valve port of the proportional reversing valve by controlling the handle so as to realize the control of the flow flowing through the proportional reversing valve.
After the engineering machinery is started, an operator adjusts the accelerator knob according to the requirement of earthwork operation, and the power source 1 can drive the main pump 2 and the pilot pump 3 to respectively supply oil for the load sensitive mechanism and the pilot oil way according to the target accelerator rotating speed transmitted by the accelerator knob. The high-pressure oil generated by the main pump 2 flows into the load-sensitive mechanism, when the handle is not input or is lower than a preset control threshold, the proportional directional valve is in a neutral position, the hydraulic oil of the main pump 2 flows into the second two-position two-way directional valve 17, at this time, the first port a of the shuttle valve 15 and the second port B of the shuttle valve 15 are connected with the hydraulic oil tank 19, the pressure of the third port C of the shuttle valve 15 is approximately zero, and the second two-position two-way directional valve 17 stabilizes the outlet pressure of the main pump 2 to be the spring control pressure of the second two-position two-way directional valve 17 through dynamic adjustment. Meanwhile, the pilot pump 3 generates high-pressure oil to flow into the first two-position three-way reversing valve 7, the high-pressure oil respectively flows into the third interface A of the first two-position three-way reversing valve 6 and the upper and lower control cavities of the first two-position three-way reversing valve 6 after being dynamically adjusted by the first two-position three-way reversing valve 6 and the second two-position three-way reversing valve 8, pressure oil with pressure similar to the pressure of the outlet of the main pump 2 is generated to control the displacement adjusting mechanism, the displacement of the main pump 2 is reduced, the minimum oil supply displacement of the system leakage amount is ensured, and the system energy consumption in the non-action process of the system is reduced.
When the handle inputs a signal higher than a preset control threshold value, the opening degrees of the valve ports of the first three-position five-way reversing valve 9 and the second three-position five-way reversing valve 10 are controlled according to the linear relation of the handle input signals, and meanwhile, the system controls the power source 1 to drive the main pump 2 and the pilot pump 3 to respectively supply oil for the load sensitive mechanism and the pilot oil way according to a target throttle signal.
The high-pressure oil generated by the main pump 2 flows into the corresponding actuator through the first and second three-position five- way selector valves 9 and 10 and the first and second pressure compensating valves 11 and 12. The pilot pump 3 generates hydraulic oil to flow into a speed sensitive valve composed of the first two-position two-way reversing valve 7 and the second two-position three-way reversing valve 8 and the differential pressure reducing valve 16, target pressure oil is generated to control the discharge capacity of the main pump 2, the outlet pressure of the main pump 2 is controlled by adjusting the volume of the main pump 2 to be higher than the maximum load pressure by a target value, and the target value is equal to the hydraulic oil pressure generated by the pilot pump 3 after the hydraulic oil flows into the speed sensitive valve composed of the first two-position two-way reversing valve 7 and the second two-position three-way reversing valve 8 and the differential pressure reducing valve 16.
For different rotating speeds of the power source 1, the displacement of the pilot pump 3 is fixed, different rotating speeds cause different output flows of the pilot pump 3, when the rotating speed of the power source 1 is higher, the pilot pump 3 generates more flows, the flows flow enters the first two-way reversing valve 7, smaller pressure difference is generated through dynamic balance adjustment of a throttling hole structure of the first two-way reversing valve 7 and flows out of the first two-way reversing valve 7, so that the outlet pressure of the first two-way reversing valve 7 is higher, the flows flow enters the third interface A of the first two-way reversing valve 6 and the upper and lower control cavities of the first two-way reversing valve 6 through the second two-way three-way reversing valve 8 and the pressure difference reducing valve 16, the main pump 2 is adjusted, so that the difference value between the outlet pressure of the main pump 2 and the system maximum load displacement is equal to the outlet pressure of the first two-way reversing valve 7, and the pressure value is higher.
When the rotating speed of the power source 1 is low, the pilot pump 3 generates less flow, the flow enters the first two-position three-way reversing valve 6, a large pressure difference is generated through dynamic balance adjustment of a throttling hole structure of the first two-position three-way reversing valve 6 and flows out of the first two-position three-way reversing valve 6, so that the outlet pressure of the first two-position three-way reversing valve 6 is small, the flow enters the third interface A of the first two-position three-way reversing valve 6 and the upper and lower control cavities of the first two-position three-way reversing valve 6 through the second two-position three-way reversing valve 8 and the pressure difference reducing valve 16, the displacement of the main pump 2 is adjusted, the difference value between the outlet pressure of the main pump 2 and the maximum system load pressure is equal to the outlet pressure of the first two-position three-way reversing valve 7, and the pressure value is small.
The corresponding relation between the valve core and the flow of the main valve under different pressure differences is changed by controlling the difference value between different outlet pressures of the main pump 2 and the maximum load pressure of the system, so that the whole throttle signal input is smaller during fine action, the rotating speed of the power source 1 is lower, a smaller output pressure value is generated by a rotating speed sensitive valve consisting of the first two-position two-way reversing valve 7 and the second two-position three-way reversing valve 8, the pressure difference value between the outlet pressure and the maximum load pressure of the main pump 2 is controlled to be smaller, the input signal and the system flow regulation have better linear control precision, the whole throttle signal input is larger during fast action, the rotating speed of the power source 1 is higher, and a larger output pressure value is generated by a rotating speed sensitive valve consisting of the first two-position two-way reversing valve 7 and the second two-position three-way reversing valve 8, the pressure difference value between the outlet pressure and the maximum load pressure of the main pump 2 is controlled to be larger, so that the flow regulating range of the input signal corresponding to the system is wider, and the system has higher action speed. And then through the mode, the system rotating speed sensitive control under different rotating speeds of the power source is realized.
In the working process of the system, pressure oil generated by the pilot pump 3 flows into the third interface P of the differential pressure reducing valve 16 after being regulated by the first two-way reversing valve 7, flows out of the first interface A of the differential pressure reducing valve 16, is fed back to a lower control cavity of the differential pressure reducing valve 16, and is used for regulating the discharge capacity of the main pump 2. An upper control cavity of the differential pressure reducing valve 16 is connected with an outlet of the main pump 2, a lower control cavity of the differential pressure reducing valve 16 is connected with a third C of the shuttle valve 15 through the throttle hole 18, a first interface A of the shuttle valve 15 and a second interface B of the shuttle valve 15 are respectively connected with load cavities of the first execution oil cylinder 13 and the second execution oil cylinder 14, the first interface A and the second interface B are used for detecting a highest working pressure cavity of a system, the high-pressure oil flows out through the third interface C of the shuttle valve 15, and the high-pressure oil is subjected to damping filtering through the throttle hole 18 and then fed back to a lower control cavity of the differential pressure reducing valve 16. The differential pressure reducing valve 16 compares the outlet pressure of the main pump 2 with the maximum load pressure, and stabilizes that the difference value between the outlet pressure and the maximum load pressure is equal to the outlet pressure of the first two-position two-way reversing valve 7 through the differential pressure reducing valve 16, so that the function of low-pass filtering is achieved, the system impact caused by severe load change is reduced, and the stability of the system is improved.
When multiple actuators of the engineering machinery act simultaneously, and the input value of the handle is high, at the moment, the flow generated by the main pump 2 even working according to the maximum displacement is not enough to ensure that the multiple actuators operate at the target high speed, and the system enters a flow saturation area. At this time, the main pump 2 maintains the difference between the outlet pressure and the maximum load pressure of the main pump 2 as a target value through displacement adjustment, and the system dynamically adjusts through the first pressure compensation valve 11 and the second pressure compensation valve 12, so that the difference between the pressure at the throttle ports of the first three-position five-way reversing valve 9 and the second three-position five-way reversing valve 10 is stabilized to be constant, and the difference between the pressure at the throttle ports of the first three-position five-way reversing valve 9 and the second three-position five-way reversing valve 10 is also made to be equal, so that when the flow is saturated, the flow flowing into each actuator is equally distributed according to the area of the throttle ports of the first three-position five-way reversing valve 9 and the second three-position five-way reversing valve 10, and the coordination of the cooperative action of multiple actuators is ensured.
Based on the above, the beneficial effects of the embodiment at least include:
(1) the target control pressure difference of the pressure compensation valve of the load sensitive mechanism is adjusted through the rotating speed sensitive valve, the valve core-flow corresponding relation of the main valve under different pressure differences is realized, and the control characteristics of different operation processes such as fine operation, large-flow operation and the like can be improved. Meanwhile, the differential pressure reducing valve 16 is introduced into the load sensitive mechanism, dynamic analog filtering is carried out on the differential pressure between the outlet pressure of the pump and the maximum load pressure, and the analog signal is used for displacement control of the pump and target compensation differential pressure control of a pressure compensation valve in the main control valve, so that the system has higher stability.
(2) The load difference is compensated through the pressure compensation valve on the rear side of the main control valve, the main control valve pressure difference of different actuators is kept to be customized, the main control valve pressure difference of different actuators is the same, the linear control degree of a system pilot input signal and the actuator target control speed is improved, and the coordination control performance of the multiple actuators in the rapid movement process is guaranteed.
The second embodiment of the invention provides a load rotating speed double-sensitive anti-flow saturation engineering mechanical device which comprises the load rotating speed double-sensitive anti-flow saturation system.
In summary, according to the load-rotation-speed dual-sensing anti-flow saturation system and the engineering mechanical device thereof provided by this embodiment, the flow matching of the hydraulic pump is realized by detecting the maximum load pressure, the difference between the outlet pressure of the hydraulic pump and the maximum load pressure is controlled to be a certain control value, the rotation speed of the power source is monitored by the rotation speed sensitive valve, and the target control pressure difference of the pressure compensation valve of the load-sensitive mechanism is adjusted by the rotation speed sensitive valve, so as to realize the valve core-flow corresponding relation of the main valve under different pressure differences, thereby solving the problem that the pressure difference value of the conventional load-sensitive system is the set value of the system spring, and the pressure difference is constant during the working process, and the given pressure difference value still cannot be well adapted to different working requirements under different working conditions; and when the flow supply of the hydraulic pump is insufficient, the flow supply of the system is insufficient, the valve port pressure difference can drop, the valve port pressure difference of the reversing valve of each actuator can be distinguished, and hydraulic oil can still not flow into each actuator according to the input control proportion.
The above is only a preferred embodiment of the present invention, and the protection scope of the present invention is not limited to the above-mentioned embodiments, and all technical solutions belonging to the idea of the present invention belong to the protection scope of the present invention.
Claims (9)
1. A load rotating speed double-sensitive anti-flow saturation system is characterized by comprising an operation component, a main pump source, a pilot control pump source, a load sensitive mechanism and a hydraulic oil tank;
the input end of the main pump source and the input end of the pilot control pump source are connected with the hydraulic oil tank;
the output end of the main pump source is connected with the input end of the load sensitive mechanism;
the output end of the pilot control pump source is connected with the control end of the load sensitive mechanism and the control end of the main pump source;
the output end of the load sensitive mechanism is connected with the control end of the pilot control pump source and the control end of the main pump source;
the output end of the load sensitive mechanism is used for connecting a plurality of executing devices;
the pilot control pump source is used for adjusting the pressure difference between the input end and the output end of the load sensitive mechanism when the main pump source receives an accelerator signal transmitted by the operating assembly;
and the load sensitive mechanism is configured to adjust the system to enter a saturation region when the handle signal transmitted by the operating assembly is higher than a preset value, and supply oil to each execution device according to the input proportion of the handle signal.
2. The load-speed dual-sensing flow-saturation resistant system according to claim 1, wherein said manipulation assembly includes an operating handle and a throttle knob, an output of said handle is electrically connected to an input of said load-sensing mechanism, and an output of said throttle knob is electrically connected to an input of said main pump source.
3. The load-speed dual-sensing anti-flow-saturation system according to claim 1, wherein said primary pump source comprises a power source, a primary pump, a first two-position three-way directional valve, a first displacement adjustment mechanism, and a second displacement adjustment mechanism;
the power source is mechanically connected with the main pump, the main pump is mechanically connected with the pilot control pump source, the load sensitive mechanism and the hydraulic oil tank pipeline, the inlet of the main pump is connected with the hydraulic oil tank pipeline, the outlet of the main pump is connected with the control port pipeline of the first displacement adjusting mechanism, the first interface of the first two-position three-way reversing valve is connected with the second displacement adjusting mechanism pipeline, the second interface of the first two-position three-way reversing valve is connected with the hydraulic oil tank pipeline, and the first two-position three-way reversing valve is connected with the load sensitive mechanism pipeline.
4. The load-speed dual-sensing anti-flow saturation system according to claim 3, wherein said pilot controlled pump source comprises a pilot pump, and a speed sensitive valve;
the inlet of the pilot pump is connected with the hydraulic oil tank through a pipeline, the outlet of the pilot pump is connected with an interface pipeline of the rotating speed sensitive valve, the input end of the rotating speed sensitive valve is connected with the hydraulic oil tank through a pipeline, and the interface of the rotating speed sensitive valve is connected with the interface of the first two-position three-way reversing valve and the input end pipeline of the load sensitive mechanism.
5. The load speed dual sensing anti-flow saturation system according to claim 4, wherein said speed sensitive valves include a first two-position, two-way directional valve, and a second two-position, three-way directional valve;
the outlet of the pilot pump is in pipeline connection with a first interface of the first two-position two-way reversing valve, a left side control cavity of the first two-position two-way reversing valve and a lower side control cavity of the second two-position three-way reversing valve, a second interface of the first two-position two-way reversing valve is in pipeline connection with a second interface of the second two-position three-way reversing valve, an upper side control cavity of the second two-position three-way reversing valve and a right side control cavity of the first two-position two-way reversing valve, a third interface of the second two-position three-way reversing valve is in pipeline connection with the hydraulic oil tank, a second interface of the first two-position two-way reversing valve is in pipeline connection with a third interface of the first two-position three-way reversing valve and an input end of the load sensing mechanism, a first interface of the second two-position three-way reversing valve is in pipeline connection with an upper control cavity of the second two-position three-way reversing valve, an input end of the load sensing mechanism, a first port of the load sensing mechanism, a second port of the load sensing mechanism, and a second port of the load sensing mechanism, And the lower side control cavity pipeline of the first two-position three-way reversing valve is connected.
6. The load-speed dual-sensing anti-flow saturation system according to claim 5, wherein said load-sensing mechanism comprises a proportional directional valve, a first pressure compensating valve, a second pressure compensating valve, an actuator, a shuttle valve, a second two-position two-way directional valve, a differential pressure reducing valve, and an orifice;
wherein an input end of the proportional reversing valve is connected with the hydraulic oil tank through a pipeline, a port of the proportional reversing valve is connected with a port of the first pressure compensation valve, a port of the second pressure compensation valve, a port of the actuator and a port of the shuttle valve through pipelines, a second port of the first pressure compensation valve and a second port of the second pressure compensation valve are connected with a port of the actuator through a pipeline, a third port of the shuttle valve is connected with a right control cavity of the first pressure compensation valve, a right control cavity of the second pressure compensation valve, a first port of the orifice and a left control cavity of the second two-position two-way reversing valve through pipelines, a lower control cavity of the differential pressure reducing valve is connected with a second port of the orifice and a first port of the differential pressure reducing valve through a pipeline, and a second port of the differential pressure reducing valve is connected with the hydraulic oil tank through a pipeline, the second interface of the second two-position two-way reversing valve is connected with the hydraulic oil tank pipeline, the main pump is connected with the first interface of the second two-position two-way reversing valve, the right control cavity of the second two-position two-way reversing valve and the upper side control cavity of the differential pressure reducing valve through pipelines, the third interface of the differential pressure reducing valve is connected with the second interface of the first two-position two-way reversing valve through pipelines, the left control cavity of the second two-position two-way reversing valve is connected with the first interface of the second two-position three-way reversing valve through pipelines, and the first interface of the differential pressure reducing valve is connected with the upper control cavity of the first two-position three-way reversing valve through pipelines.
7. The load-speed dual-sensitivity flow-saturation resistant system according to claim 6, wherein said proportional directional valve comprises a first three-position five-way directional valve, and a second three-position five-way directional valve;
wherein a first interface of the first three-position five-way reversing valve is connected with a first interface of the second three-position five-way reversing valve and the hydraulic oil tank pipeline, a second interface of the first three-position five-way reversing valve is connected with a first interface of the first pressure compensation valve and a left side control cavity pipeline of the first pressure compensation valve, a third interface of the first three-position five-way reversing valve is connected with an interface of the actuator, a fourth interface of the first three-position five-way reversing valve is connected with the first interface pipeline of the shuttle valve, a second interface of the second three-position five-way reversing valve is connected with the first interface of the second pressure compensation valve and the left side control cavity pipeline of the second pressure compensation valve, a third interface of the second three-position five-way reversing valve is connected with the interface pipeline of the actuator, and a fourth interface of the second three-position five-way reversing valve is connected with the second interface pipeline of the shuttle valve, the main pump is connected with a fifth interface of the first three-position five-way reversing valve and a fifth interface of the second three-position five-way reversing valve through pipelines.
8. The load-speed dual-sensing anti-flow saturation system according to claim 7, wherein said actuator comprises a first actuator cylinder, a second actuator cylinder;
the third interface of the first three-position five-way reversing valve is connected with the first interface pipeline of the first execution oil cylinder, the second interface of the first pressure compensation valve is connected with the second interface pipeline of the first execution oil cylinder, the third interface of the second three-position five-way reversing valve is connected with the first interface pipeline of the second execution oil cylinder, and the second interface of the second pressure compensation valve is connected with the second interface pipeline of the second execution oil cylinder.
9. A load rotation speed double-sensitive anti-flow-saturation engineering mechanical device, which is characterized by comprising the load rotation speed double-sensitive anti-flow-saturation system according to any one of claims 1 to 8.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210372706.5A CN114658708B (en) | 2022-04-11 | Load rotating speed double-sensitive anti-flow saturation system and engineering mechanical device thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210372706.5A CN114658708B (en) | 2022-04-11 | Load rotating speed double-sensitive anti-flow saturation system and engineering mechanical device thereof |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN114658708A true CN114658708A (en) | 2022-06-24 |
| CN114658708B CN114658708B (en) | 2024-07-02 |
Family
ID=
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115992841A (en) * | 2022-12-08 | 2023-04-21 | 重庆大学 | Flow self-compensating load-sensitive pump valve coordinated electro-hydraulic system and control method |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5305863A (en) * | 1992-12-30 | 1994-04-26 | Eaton Corporation | Clutch assembly for an automatic mechanical transmission |
| JP2009019662A (en) * | 2007-07-10 | 2009-01-29 | Komatsu Ltd | Pressure oil supply control device and construction equipment |
| CN103267034A (en) * | 2013-05-10 | 2013-08-28 | 浙江大学 | Load sensitive hydraulic system with compensation valve energy recovery function |
| CN204163621U (en) * | 2014-10-22 | 2015-02-18 | 湖南优力特重工有限公司 | A kind of outer combining hydraulic system of valve of load-sensitive |
| CN105221506A (en) * | 2015-09-18 | 2016-01-06 | 徐州工业职业技术学院 | A kind of load-sensitive valve and load-sensitive hydraulic system |
| CN105298989A (en) * | 2015-11-13 | 2016-02-03 | 燕山大学 | Fault simulation hydraulic control system for electro-hydraulic servo system |
| CN106759621A (en) * | 2017-01-04 | 2017-05-31 | 浙江高宇液压机电有限公司 | Load-sensitive formula loading machine determines variable delivery hydraulic system |
| CN112746996A (en) * | 2019-10-31 | 2021-05-04 | 中联重科股份有限公司 | Load sensitive system and engineering hoisting machinery |
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5305863A (en) * | 1992-12-30 | 1994-04-26 | Eaton Corporation | Clutch assembly for an automatic mechanical transmission |
| JP2009019662A (en) * | 2007-07-10 | 2009-01-29 | Komatsu Ltd | Pressure oil supply control device and construction equipment |
| CN103267034A (en) * | 2013-05-10 | 2013-08-28 | 浙江大学 | Load sensitive hydraulic system with compensation valve energy recovery function |
| CN204163621U (en) * | 2014-10-22 | 2015-02-18 | 湖南优力特重工有限公司 | A kind of outer combining hydraulic system of valve of load-sensitive |
| CN105221506A (en) * | 2015-09-18 | 2016-01-06 | 徐州工业职业技术学院 | A kind of load-sensitive valve and load-sensitive hydraulic system |
| CN105298989A (en) * | 2015-11-13 | 2016-02-03 | 燕山大学 | Fault simulation hydraulic control system for electro-hydraulic servo system |
| CN106759621A (en) * | 2017-01-04 | 2017-05-31 | 浙江高宇液压机电有限公司 | Load-sensitive formula loading machine determines variable delivery hydraulic system |
| CN112746996A (en) * | 2019-10-31 | 2021-05-04 | 中联重科股份有限公司 | Load sensitive system and engineering hoisting machinery |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115992841A (en) * | 2022-12-08 | 2023-04-21 | 重庆大学 | Flow self-compensating load-sensitive pump valve coordinated electro-hydraulic system and control method |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US11131328B2 (en) | Load-sensing multi-way valve with variable differential pressure | |
| CN105221506B (en) | A kind of load-sensitive valve and load-sensitive hydraulic system | |
| WO2020006932A1 (en) | Bucket leveling system for aerial work truck | |
| CN108412829B (en) | Load sensitive type multi-way valve with independently adjustable inlet and outlet throttling edges | |
| CN109882462B (en) | Hydraulic control proportion and load sensitivity fusion variable pump and hydraulic control intelligent flow distribution system | |
| US11168713B2 (en) | Valve arrangement for pressure medium supply of a hydraulic consumer | |
| CN114622618A (en) | Novel load rotating speed double-sensitive system, engineering mechanical device and control method thereof | |
| CN111255007B (en) | Loader constant-variable hydraulic system based on load signal direct control | |
| CN113494111B (en) | Main control valve, fixed variable hydraulic system and loader | |
| JPH0419406A (en) | Hydraulic working circuit | |
| CN108716491A (en) | A kind of 3 position-5 way load port independent control multi-way valve with O-shaped Median Function | |
| CN113027847A (en) | Flow distribution control method, equipment and device of hydraulic system and hydraulic system | |
| CN114658708B (en) | Load rotating speed double-sensitive anti-flow saturation system and engineering mechanical device thereof | |
| CN114658708A (en) | Load rotating speed double-sensitive anti-flow saturation system and engineering mechanical device thereof | |
| CN215257058U (en) | Flow distribution control system | |
| CN215257059U (en) | Flow regulation control system | |
| CN108035945A (en) | Control valve group for the output of quantitative system flow proportional | |
| CN207750316U (en) | Control valve group for the output of quantitative system flow proportional | |
| JP3083152B2 (en) | Hydraulic drive for construction machinery | |
| CN114623118A (en) | Load-sensitive hydraulic transmission system and method and engineering mechanical device thereof | |
| CN114623118B (en) | Load-sensitive hydraulic transmission system, method and engineering mechanical device thereof | |
| CN113882460B (en) | Compensator for excavator rotary working device | |
| CN108661965B (en) | Three-position five-way load port independent control multi-way valve with Y-shaped neutral position function | |
| CN114857121B (en) | Fixed-variable multi-way valve and hydraulic system thereof | |
| CN218757710U (en) | Negative flow control hydraulic system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant |