CN208634123U - It is directly driven using double pump and the hydraulic crawler excavator dynamical system of the automatic changing-over of differential F.F. - Google Patents
It is directly driven using double pump and the hydraulic crawler excavator dynamical system of the automatic changing-over of differential F.F. Download PDFInfo
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- CN208634123U CN208634123U CN201821033489.2U CN201821033489U CN208634123U CN 208634123 U CN208634123 U CN 208634123U CN 201821033489 U CN201821033489 U CN 201821033489U CN 208634123 U CN208634123 U CN 208634123U
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Abstract
The utility model provides a kind of directly drive using double pump and the hydraulic crawler excavator dynamical system of the automatic changing-over of differential F.F., control instruction is issued to the driver by the controller to control driving motor revolving speed, realize that the revolving speed to coaxially connected first two-way quantitative pump and the second two-way quantitative pump controls, to realize flow control, avoid conventional hydraulic flow control valve, driving motor itself has revolving speed simultaneously, torque feedback, reduce demand sensor, realize the changing-over of differential F.F. automatically by first control valve, element is opposite to be reduced, the robustness of raising system.
Description
Technical field
It is directly driven the utility model relates to the field of energy-saving technology of hydraulic crawler excavator more particularly to a kind of use double pump and differential
The hydraulic crawler excavator dynamical system of the automatic changing-over of F.F..
Background technique
With being on the rise for energy shortage in world wide and problem of environmental pollution, energy-conserving and emission-cutting technology is to study at present
Hot spot.Hydraulic crawler excavator is a kind of biggish engineering machinery of power ratio, but the overall utilization of its energy is lower.Hydraulic excavating
Machine realizes that energy saving, reduction discharge is always the target that industry is laid siege to.Hybrid power actuation techniques and electric drive technology
It is current research hotspot.
Current excavator still uses engine-constant displacement pump-multi-way valve-actuator drive system, driven by engine
Hydraulic energy is assigned to each executing agency by multi-way valve by hydraulic pump, and hydraulic system is the valve control principle based on open type, great Liang Neng
While there is a large amount of linear loss and local losses in this process on restriction and overflow in amount consumption, i.e., pipeline portions,
Pressure loss caused by hydraulic valve etc..The hydraulic system efficiency of engineering machinery is about 30% or so, a large amount of hydraulic loss of energy
After be converted into thermal energy and cause system heat generation, system effectiveness is lower, and is not easy to realize hybrid power driving or pure electric drive.
Utility model content
The technical problems to be solved in the utility model is to provide a kind of directly drive using double pump and the automatic changing-over of differential F.F.
Hydraulic crawler excavator dynamical system, the differential F.F. in low torque, to improve production efficiency.
The utility model is realized in this way: it is directly driven using double pump and the hydraulic excavating mechanomotive force of the automatic changing-over of differential F.F.
System, including controller and an at least hydraulic module, the hydraulic module include hydraulic cylinder, the first two-way quantitative pump, second
Two-way quantitative pump, the first control valve, the second control valve, accumulator, driver and driving motor；
The hydraulic cylinder includes cylinder body, piston and piston rod, and one end of the piston rod is fixedly connected on the piston, institute
It states piston air-tightness to be slidably connected in the cylinder body, and the cylinder interior is divided into first chamber and by the piston
Two chambers；
The first two-way quantitative pump includes the first driving end, the first drain tap, first port and second port；Described
Two two-way quantitatives pump includes the second driving end, the second drain tap, third port and the 4th port；First control valve includes the
Five ports and the 6th port；Second control valve includes the 7th port and the 8th port；First driving end, the second driving
End is connected to the output end of the driving motor, is connected to institute after the first port, third port, the 7th port are in parallel
Accumulator is stated, is connected to the first chamber, the 4th port, the 8th end after the second port is in parallel with the fifth port
The second chamber is connected to after mouth, the 6th port are in parallel；First drain tap is connected to the first port and the accumulation of energy
Between device, second drain tap is connected between the third port and the 7th port；
The driver is connected to driving motor, and the driver and the first control valve are communicatively coupled to the control respectively
Device.
Further, the hydraulic module further includes third control valve and the 4th control valve, and the third control valve includes
9th port and the tenth port, the 4th control valve include the tenth Single port and the tenth Two-port netwerk；The second port connection
In the 9th port, the first chamber, the 4th port are connected to after the tenth port is in parallel with the fifth port
With the 8th port it is in parallel after be connected to the tenth Single port, the tenth Two-port netwerk and the 6th port it is in parallel after connect
Lead to the second chamber.
Further, the hydraulic module further includes the first valve group and the second valve group；First valve group includes first single
To valve and the first safety valve；Second valve group includes second one-way valve and the second safety valve；The entrance of first check valve
And be connected between the first port and accumulator after the outlet parallel connection of first safety valve, first check valve goes out
It is connected between the tenth port and fifth port after the entrance of mouth and first safety valve is in parallel；The second one-way valve
Entrance and second safety valve outlet it is in parallel after be connected between the third port and the 7th port, described second is single
To the outlet of valve and the entrance of second safety valve it is in parallel after be connected between the 6th port and the tenth Two-port netwerk.
Further, first control valve, the second control valve, the third control valve, the 4th control valve are respectively two
Position two-way electromagnetic valve.
Further, first control valve, the second control valve, the third control valve, the 4th control valve are respectively two
Position two-way plug-in valve.
Further, the driving motor is servo motor, and the driver is servo-driver.
It further, further include power supply device, the controller is electrically connected in power supply dress per the driver
It sets.
Further, there are three the hydraulic modules.
The utility model have the advantages that the utility model provide it is a kind of using double pump directly drives and differential F.F. oneself move
The hydraulic crawler excavator dynamical system connect issues control instruction by the controller and turns to the driver to control driving motor
Speed realizes that the revolving speed to coaxially connected first two-way quantitative pump and the second two-way quantitative pump controls, to realize flow
Control, avoids conventional hydraulic flow control valve, while driving motor itself has revolving speed, torque feedback, and reducing sensor needs
It asks；On the other hand, the changing-over that first control valve realizes differential F.F. automatically is controlled by the controller, element is opposite to be subtracted
It is few, the robustness of system is improved, and improve production efficiency.
Detailed description of the invention
The utility model is further described in conjunction with the embodiments with reference to the accompanying drawings.
Fig. 1 is the schematic diagram of dynamical system described in the utility model.
Fig. 2 is the schematic illustration of operating condition one described in the utility model.
The schematic illustration of hydraulic module when the unloaded differential F.F. of Fig. 3 operating condition two described in the utility model.
Fig. 4 is the schematic illustration of hydraulic module when the heavy duty of operating condition two described in the utility model is advanced.
Fig. 5 is the schematic illustration of operating condition three described in the utility model.
Fig. 6 is the schematic illustration of operating condition four described in the utility model.
Fig. 7 is the effect diagram of dynamical system described in the utility model.
In figure: 10, controller；20, hydraulic module, 201, hydraulic cylinder, 2011, cylinder body；2012, piston；2013, piston
Bar；2014, first chamber；2015, second chamber；202, the first two-way quantitative pumps；2021, the first driving end；2022, it first lets out
Hydraulic fluid port；2023, first port；2024, second port；203, the second two-way quantitative pumps；2031, the second driving end；2032, second
Drain tap；2033, third port；2034, the 4th port；204, the first control valve；2041, fifth port；2042, the 6th end
Mouthful；205, the second control valve；2051, the 7th port；2052, the 8th port；206, accumulator；207, driver；208, it drives
Motor；209, third control valve；2091, the 9th port；2092, the tenth port；210, the 4th control valve；2101, the tenth one end
Mouthful；2102, the tenth Two-port netwerk；211, the first valve group；2111, the first check valve；2112, the first safety valve；212, the second valve group；
2121, second one-way valve；2122, the second safety valve；30, swing arm；40, dipper；50, scraper bowl；60, power supply device.
Specific embodiment
It please refers to shown in Fig. 1 to Fig. 7, the utility model provides a kind of directly drive using double pump and the automatic changing-over of differential F.F.
Hydraulic crawler excavator dynamical system, including controller 10 and an at least hydraulic module 20, the hydraulic module 20 include hydraulic cylinder
201, the first two-way quantitative pumps the 202, second two-way quantitative and pumps the 203, first control valve 204, the second control valve 205, accumulator
206, driver 207 and driving motor 208；
The hydraulic cylinder 201 includes cylinder body 2011, piston 2012 and piston rod 2013, and one end of the piston rod 2013 is solid
Surely it is connected to the piston 2012,2012 air-tightness of piston is slidably connected in the cylinder body 2011, and the work
Plug 2012 will be divided into first chamber 2014 and second chamber 2015 inside the cylinder body 2011；
The first two-way quantitative pump 202 includes the first driving end 2021, the first drain tap 2022,2023 and of first port
Second port 2024；The second two-way quantitative pump 203 includes the second driving end 2031, the second drain tap 2032, third port
2033 and the 4th port 2034；First control valve 204 includes fifth port 2041 and the 6th port 2042；Second control
Valve 205 processed includes the 7th port 2051 and the 8th port 2052；First driving end 2021, second drives end 2031 to connect respectively
It is connected to the output end of the driving motor 208, after the first port 2023, third port 2033,2051 parallel connection of the 7th port
It is connected to the accumulator 206, is connected to the first chamber after the second port 2024 and 2041 parallel connection of fifth port
2014, the second chamber 2015 is connected to after the 4th port 2034, the 8th port 2052,2042 parallel connection of the 6th port；Institute
It states the first drain tap 2022 to be connected between the first port 2023 and the accumulator 206, second drain tap 2032
It is connected between the third port 2033 and the 7th port 2051；Pass through first drain tap 2022 and the second draining
Mouth 2032 can prevent the first two-way quantitative pump 202 and the second two-way quantitative pump 203 because hypertonia leads to the shell of pump
Rupture；
The driver 207 is connected to driving motor 208, and the driver 207 and the first control valve 204 distinguish communication link
It is connected to the controller 10.
The utility model issues control instruction to the driver 207 to control driving motor by the controller 10
208 revolving speeds realize that the revolving speed to coaxially connected first two-way quantitative pump 202 and the second two-way quantitative pump 203 controls, from
And realize flow control, major loop is very short, and avoids energy loss caused by conventional hydraulic flow control valve, it may be unnecessary to cold
But device also avoids the restriction loss and spill losses of system, and system effectiveness is higher, at the same driving motor 208 itself have turn
Speed, torque feedback, reduce demand sensor, realize the changing-over of unloaded differential F.F. automatically by first control valve 204,
Element is opposite to be reduced, so that hardware cost is lower, simultaneity factor is simpler, improves the robustness of system, and improves production effect
Rate.The flow of the first chamber 2014 and second chamber 2015 is balanced by the accumulator 206.The utility model
Potential energy recycling when also for over-running load provides condition.
In specific implementation, a preferred embodiment: the hydraulic module 20 further includes third control valve 209 and the 4th control
Valve 210 processed, the third control valve 209 include the 9th port 2091 and the tenth port 2092, and the 4th control valve 210 includes
Tenth Single port 2101 and the tenth Two-port netwerk 2102；The second port 2024 is connected to the 9th port 2091, and described
It is connected to the first chamber 2014 behind ten ports 2092 and 2041 parallel connection of fifth port, the 4th port 2034 and described
The tenth Single port 2101, the tenth Two-port netwerk 2102 and the 6th port are connected to after 8th port, 2052 parallel connection
The second chamber 2015 is connected to after 2042 parallel connections.It will be described hydraulic by the third control valve 209 and the 4th control valve 210
Cylinder 201 locks, and avoids the sliding due to caused by the leakage of first two-way quantitative pump 202 or the second two-way quantitative pump 203.
The hydraulic module 20 further includes the first valve group 211 and the second valve group 212；First valve group 211 includes first
Check valve 2111 and the first safety valve 2112；Second valve group 212 includes second one-way valve 2121 and the second safety valve 2122；
The first port is connected to after the outlet of the entrance of first check valve 2111 and first safety valve 2112 is in parallel
Between 2023 and accumulator 206, behind the outlet of first check valve 2111 and the entrance parallel connection of first safety valve 2112
It is connected between the tenth port 2092 and fifth port 2041；The entrance of the second one-way valve 2121 and second peace
It is connected between the third port 2033 and the 7th port 2051 after the outlet of full valve 2122 is in parallel, the second one-way valve
The 6th port 2042 and the tenth Two-port netwerk are connected to after 2121 outlet and the entrance parallel connection of second safety valve 2122
Between 2102.Prevent emptying phenomenon in low pressure by first valve group 211 and the second valve group 212, in high pressure into
Extra oil liquid is stored into the accumulator 206 by row pressure release, specifically, working as the first chamber 2014 or second chamber
When 2015 pressure is low, corresponding first check valve 2111 or second one-way valve 2121 are connected, and oil liquid is from the accumulator
It is added in 206 in the first chamber 2014 or second chamber 2015, when the first chamber 2014 or second chamber 2015
Hypertonia when, first safety valve 2112 corresponding at this time or the second safety valve 2122 conducting, carry out pressure release, will be extra
Oil liquid be flowed into the accumulator 206, guarantee safety.
First control valve 204, the second control valve 205, the third control valve 209, the 4th control valve 210 are respectively
Two-position two-way solenoid valve.Solenoid valve is used when small flow, is mainly used in mini-excavator in practice.
First control valve 204, the second control valve 205, the third control valve 209, the 4th control valve 210 are respectively
Bi-bit bi-pass inserted valve.Bi-bit bi-pass inserted valve is used when big flow, be mainly used in practice it is small, in, large-scale dig
Pick machine.
The driving motor 208 is servo motor 208, and the driver 207 is servo-driver 207, can make control speed
It is very accurate to spend precision.
It further include power supply device 60, the controller 10 is electrically connected per the driver 207 in the power supply device
60.For the utility model in the case where over-running load, the first two-way quantitative pump 202 and the second two-way quantitative pump 203 conducts
Motor uses, and can be that electric energy is stored into the power supply device 60 by the potential energy for loading feedback, be reused, saved
The about energy.
There are three the hydraulic modules 20, three hydraulic modules 20 connect one to one in excavator swing arm 30,
Dipper 40, scraper bowl 50 realize that three independently drives, facilitate control, while high degree shortens pipeline, can be institute
It states hydraulic module 20 and is made into hydraulic packet form, it is easy for installation, it is small in size.
Control principle:
Because of the presence of the piston rod 2013, the first chamber 2014 and second chamber 2015 are unsymmetric structure,
So that the maximum volume of the first chamber 2014 is greater than the maximum volume of the second chamber 2015, the hydraulic cylinder 201 is
Asymmetrical cylinder 201, when oil liquid is transported to the second chamber 2015 from the first chamber 2014, it is extra that oil liquid has,
It needs to store extra oil liquid into the accumulator 206, and when oil liquid is transported to described the from the second chamber 2015
When one chamber 2014, the oil liquid in the accumulator 206 is needed to add in the first chamber 2014.
Please refer to shown in Fig. 2 to Fig. 6, the utility model has following operating condition in operation: F is applied to institute for load in figure
The external force of piston rod 2013 is stated, v is the speed of service of the piston rod 2013；Hydraulic coupling direction and external force F's is contrary；Institute
The load that piston rod 2013 is connected to excavator is stated, the load of excavator can generate potential energy during the work time；Described first pair
It both can be used as pump to constant displacement pump 202 and the second two-way quantitative pump 203, and can also be used as motor and generate electricity；
Positive value load: hydraulic coupling direction is identical as the direction of v, and the piston rod 2013 is stretched out or retracted, at this time the electricity
Source device 60 exports electric energy, and the controller 10 controls the driver 207 and the servo motor 208 is driven to drive described first
203 rotation of two-way quantitative pump 202 and the second two-way quantitative pump, the piston rod 2013 export energy to load；
Over-running load: contrary, the stretching of piston rod 2013 or the retraction in hydraulic coupling direction and v, load feedback energy
It measures to the piston rod 2013, the first two-way quantitative pump 202 and the second two-way quantitative pump 203 is made by hydraulic circuit
It is used as motor, is in generating state, stores energy to the power supply device 60, be recycled.
Operating condition 1 please refers to shown in Fig. 2: in the case where for over-running load, the piston rod 2013 is retracted, the piston rod
2013 by the pressure loaded, and F is pressure at this time, the potential energy of load is passed to the piston rod 2013, and then by hydraulic
Circuit drives the first two-way quantitative pump 202 and the second two-way quantitative pump 203 to generate electricity, by power storage to the power supply
It in device 60, is recycled, has saved energy, at this time the flow direction of the oil liquid in the hydraulic module 20 are as follows: described first
Oil liquid in chamber 2014 is transported to the finally conveying of the second two-way quantitative pump 203 by first two-way quantitative pump 202
To the first chamber 2014, while extra oil liquid flows into the accumulator 206, to realize the first chamber 2014
With the flow equilibrium in second chamber 2015.
Operating condition 2 please refers to shown in Fig. 3 and Fig. 4: there are two types of operating conditions in the case where stretching out for positive value load:
1. operating condition when small load differential F.F., please refers to shown in Fig. 3；F is F at this timeIt is small, speed V is VFastly, institute at this time
It states controller 10 and controls the conducting of the first control valve 204, oil liquid passes through first control valve from the second chamber 2015
204 flow into the first chambers 2014, realize and automatically switch to carry out differential F.F., according to the torque feedback of driving motor 208,
Differential F.F. is used when low torque, to improve production efficiency；Simultaneously on the one hand, a part of oil liquid is pumped in second two-way quantitative
203 flow to and flow back into the second two-way quantitative pump 203 after second control valve 205 again, idle cycle are formed, by described
Second control valve 205 can prevent that emptying phenomenon occurs in idle cycle, and on the other hand, a part of oil liquid is from the accumulator
It is transported to the first chamber 2014 after flowing into the first two-way quantitative pump 202 in 206, flow supplement is carried out, to realize
Flow equilibrium between the first chamber 2014 and second chamber 2015.
2. operating condition when positive value heavy load load piston bar stretches out, please refers to shown in Fig. 4；F is F at this timeGreatly, speed V is VSlowly,
First control valve 204 is closed at this time, and oil liquid is pumped from the second chamber 2015 followed by second two-way quantitative
203, the first two-way quantitative pump 202 finally flows into the first chamber 2014, while a part of oil liquid is from the accumulator 206
It is transported to the first chamber 2014 after flowing into first two-way quantitative pump 202, carries out flow supplement, to realize described the
Flow equilibrium between one chamber 2014 and second chamber 2015.By the torque internal feedback of driving motor 208, realize differential fast
Into the automatic changing-over advanced with heavy duty, production efficiency is improved.
Operating condition 3 please refers to shown in Fig. 5: in the case where for over-running load, the piston rod 2013 stretches out, the piston rod
2013 by the pulling force loaded, and F is pulling force at this time, the potential energy of load is passed to the piston rod 2013, and then by hydraulic
Circuit drives the first two-way quantitative pump 202 and the second two-way quantitative pump 203 to generate electricity, by power storage to the power supply
It in device 60, is recycled, has saved energy；At this point, the controller 10 controls the driver 207 and then controls institute
It states servo motor 208 and drives the first two-way quantitative pump 202 and the second two-way quantitative pump 203, by the second chamber 2015
Oil liquid first two-way quantitative pump 202 be transported to by second two-way quantitative pump 203 be finally transported to described first
Chamber 2014 also needs the oil liquid in the accumulator 206 to be supplemented at this time, to realize the first chamber 2014 and
Flow equilibrium in two chambers 2015.
Operating condition 4 please refers to shown in Fig. 6: in the case where for positive value load, the piston rod 2013 is retracted, the piston rod
2013 by the pulling force loaded, and F is pulling force, the flow direction of the oil liquid in the hydraulic module 20 are as follows: the first chamber at this time
Oil liquid in 2014 is transported to the second two-way quantitative pump 202 by first two-way quantitative pump 202 and is finally transported to institute
Second chamber 2015 is stated, while the extra oil liquid of the first chamber 2014 being flowed into the accumulator 206, to realize institute
State the flow equilibrium in first chamber 2014 and second chamber 2015.
The advantages of the utility model: independent double pump single motor hydraulic-driven mould is provided for each hydraulic cylinder of hydraulic crawler excavator
Block, the fuel tank in hydraulic module 20 is substituted using low pressure accumulator 206, is connect using double pump/motors with driving motor 208, logical
Motor 208 of overdriving adjusts the speed and changes direction to control hydraulic cylinder 201；By the torque internal feedback of driving motor 208, it is poor to realize
The automatic changing-over that dynamic F.F. and heavy duty are advanced；More easily realize hybrid power driving or pure electric drive；With conventional motive system
It compares, system effectiveness is higher, and fluid pressure line has been greatly shortened, and reduces the pressure loss, and reduce leakage point, improves system robust
Property；Power is provided as needed, without standby；Realize the recycling of gravitional force；When the piston rod 2013 of hydraulic cylinder 201 stretches out,
According to the torque feedback of driving motor 208, the differential F.F. in low torque, to improve production efficiency.
Although those familiar with the art answers the foregoing describe specific embodiment of the present utility model
Working as understanding, we are merely exemplary described specific embodiment, rather than for the limit to the scope of the utility model
Fixed, those skilled in the art modification and variation equivalent made by the spirit according to the utility model all should
Cover in the scope of the claimed protection of the utility model.
Claims (8)
1. use double pump directly drives and the hydraulic crawler excavator dynamical system of the automatic changing-over of differential F.F., it is characterised in that: including power supply
Device, controller and an at least hydraulic module, the hydraulic module includes hydraulic cylinder, the first two-way quantitative pump, second two-way
Constant displacement pump, the first control valve, the second control valve, accumulator, driver and driving motor；
The hydraulic cylinder includes cylinder body, piston and piston rod, and one end of the piston rod is fixedly connected on the piston, the work
Plug air-tightness is slidably connected in the cylinder body, and the cylinder interior is divided into first chamber and the second chamber by the piston
Room；
The first two-way quantitative pump includes the first driving end, the first drain tap, first port and second port；Described second pair
It include the second driving end, the second drain tap, third port and the 4th port to constant displacement pump；First control valve includes the 5th end
Mouth and the 6th port；Second control valve includes the 7th port and the 8th port；First driving end, the second driving end point
It is not connected to the output end of the driving motor, is connected to the storage after the first port, third port, the 7th port are in parallel
Can device, the second port and the fifth port it is in parallel after be connected to the first chamber, the 4th port, the 8th port,
The second chamber is connected to after 6th port is in parallel；First drain tap be connected to the first port and the accumulator it
Between, second drain tap is connected between the third port and the 7th port；
The driver is connected to the power supply device and driving motor, and the controller is connected to the power supply device,
The driver and the first control valve are communicatively coupled to the controller respectively.
It is directly driven using double pump and the hydraulic crawler excavator dynamical system of the automatic changing-over of differential F.F. 2. according to claim 1,
It is characterized by: the hydraulic module further includes third control valve and the 4th control valve, the third control valve includes the 9th end
Mouth and the tenth port, the 4th control valve include the tenth Single port and the tenth Two-port netwerk；The second port is connected to described
It is connected to the first chamber after 9th port, the tenth port and the fifth port are in parallel, the 4th port and described
Be connected to the tenth Single port after 8th port is in parallel, the tenth Two-port netwerk and the 6th port it is in parallel after be connected to described in
Second chamber.
It is directly driven using double pump and the hydraulic crawler excavator dynamical system of the automatic changing-over of differential F.F. 3. according to claim 2,
It is characterized by: the hydraulic module further includes the first valve group and the second valve group；First valve group include the first check valve and
First safety valve；Second valve group includes second one-way valve and the second safety valve；The entrance of first check valve and described
It is connected between the first port and accumulator after the outlet of first safety valve is in parallel, the outlet of first check valve and institute
It is connected between the tenth port and fifth port after stating the entrance parallel connection of the first safety valve；The entrance of the second one-way valve
And be connected between the third port and the 7th port after the outlet parallel connection of second safety valve, the second one-way valve
It is connected between the 6th port and the tenth Two-port netwerk after the entrance of outlet and second safety valve is in parallel.
It is directly driven using double pump and the hydraulic crawler excavator dynamical system of the automatic changing-over of differential F.F. 4. according to claim 3,
It is characterized by: first control valve, the second control valve, the third control valve, the 4th control valve are respectively bi-bit bi-pass
Solenoid valve.
It is directly driven using double pump and the hydraulic crawler excavator dynamical system of the automatic changing-over of differential F.F. 5. according to claim 3,
It is characterized by: first control valve, the second control valve, the third control valve, the 4th control valve are respectively bi-bit bi-pass
Inserted valve.
It is directly driven using double pump and the hydraulic crawler excavator dynamical system of the automatic changing-over of differential F.F. 6. according to claim 1,
It is characterized by: the driving motor is servo motor, the driver is servo-driver.
It is directly driven using double pump and the hydraulic crawler excavator dynamical system of the automatic changing-over of differential F.F. 7. according to claim 1,
It is characterized by also including power supply device, the controller is electrically connected per the driver in the power supply device.
It is directly driven using double pump and the hydraulic crawler excavator of the automatic changing-over of differential F.F. 8. according to any one of claims 1 to 7
Dynamical system, it is characterised in that: there are three the hydraulic modules.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201821033489.2U CN208634123U (en) | 2018-07-02 | 2018-07-02 | It is directly driven using double pump and the hydraulic crawler excavator dynamical system of the automatic changing-over of differential F.F. |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201821033489.2U CN208634123U (en) | 2018-07-02 | 2018-07-02 | It is directly driven using double pump and the hydraulic crawler excavator dynamical system of the automatic changing-over of differential F.F. |
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| Publication Number | Publication Date |
|---|---|
| CN208634123U true CN208634123U (en) | 2019-03-22 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201821033489.2U Expired - Fee Related CN208634123U (en) | 2018-07-02 | 2018-07-02 | It is directly driven using double pump and the hydraulic crawler excavator dynamical system of the automatic changing-over of differential F.F. |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108533546A (en) * | 2018-07-02 | 2018-09-14 | 福建工程学院 | It is directly driven using double pump and the hydraulic crawler excavator dynamical system of the automatic changing-over of differential F.F. |
| CN111271327A (en) * | 2020-01-23 | 2020-06-12 | 福建工程学院 | Independent composite control hydraulic system |
| CN111412198A (en) * | 2019-12-29 | 2020-07-14 | 福建工程学院 | Speed closed-loop control method for variable-rotation-speed dual-pump cylinder control closed system under four-quadrant working condition |
-
2018
- 2018-07-02 CN CN201821033489.2U patent/CN208634123U/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108533546A (en) * | 2018-07-02 | 2018-09-14 | 福建工程学院 | It is directly driven using double pump and the hydraulic crawler excavator dynamical system of the automatic changing-over of differential F.F. |
| CN108533546B (en) * | 2018-07-02 | 2023-06-27 | 福建工程学院 | Hydraulic excavator power system adopting double-pump direct drive and differential fast forward automatic switching |
| CN111412198A (en) * | 2019-12-29 | 2020-07-14 | 福建工程学院 | Speed closed-loop control method for variable-rotation-speed dual-pump cylinder control closed system under four-quadrant working condition |
| CN111271327A (en) * | 2020-01-23 | 2020-06-12 | 福建工程学院 | Independent composite control hydraulic system |
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