CN208009522U - A kind of electric drive loading machine electronic-hydraulic complex control system - Google Patents
A kind of electric drive loading machine electronic-hydraulic complex control system Download PDFInfo
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Abstract
The utility model discloses a kind of electric drive loading machine electronic-hydraulic complex control systems, the control system is by entire car controller, preferential steering hydraulic system, driving system and detection feedback unit composition, the entire car controller receives the gear signal of driver's input, accelerator pedal signal and the steering wheel tach signal of feedback unit detection, the pressure signal of the displacement signal and steering circuit and performance loop of swing arm handle and scraper bowl handle, after analyzing processing, running motor controller output control signal in work drive motor controller and driving system into preferential steering hydraulic system respectively, and then control work drive motor and running motor export power outward, and further control work drive motor switches between general mode and energy saver mode.The utility model reduces overflow, restriction loss and the median load loss of hydraulic system, improves the working efficiency of vehicle.
Description
Technical field
The utility model belongs to engineering truck control technology field, is suitable for electric drive loading machine, and in particular to Yi Zhong electricity
Drive loading machine electronic-hydraulic complex control system.
Background technology
Loading machine is widely used in agricultural, mine, building, water conservancy, the fields such as build the road, in state as a kind of engineering truck
Family's Important Project, civil engineering and national defense construction etc. play important function.It is increasingly tight in energy shortage and environmental pollution
Under the situation of weight, the development of energy-conserving and emission-cutting technology also receives country and enterprise more and more concern and attention, and electric
Actuation techniques also because of it efficiently, environmental protection, low noise and the advantages that flexible structure, response quickly, shown in engineer application
Its huge value and good development prospect.
Loading machine mostly uses engine driving fluid torque-converter at present, and torque-converters imparts power to hydraulic pump and speed change again
Device, to which drive hydraulic system principle and driving system work；Hydraulic system is basically divided into double quantitative systems, determine variable system and
Entire variable system.
First, there are mechanical couplings with hydraulic system for the driving system of conventional load machine, need not be turned in transition
And in the case of equipment is idle, hydraulic system can be caused to there is certain middle position off-load loss；
Secondly, since hydraulic pump discharge is fixed in quantitative system, it is easy to appear outputs to flow during the work time for loading machine
Amount and the unmatched phenomenon of loading demand, cause Fuel Economy to reduce, and hydraulic fluid temperature increases, and hydraulic system
Spill losses is serious, and working efficiency is relatively low.
Finally, variable pump systems are although efficient, but complicated, and cost is higher, and there is also one in practical applications
Fixed limitation.
Invention content
Defect present in for the above-mentioned prior art, it is electric-hydraulic combined that the utility model provides a kind of electric drive loading machine
Control system, overflow, restriction loss and median load to reduce hydraulic system are lost, and vehicle working efficiency is improved.In conjunction with
Figure of description, the technical solution of the utility model are as follows：
A kind of electric drive loading machine electronic-hydraulic complex control system, the control system by entire car controller, preferentially turn to liquid
Pressure system, driving system and detection feedback unit composition；
In the preferential steering hydraulic system, work drive motor controller 4, work drive motor 5, constant displacement pump 6 and pressure-gradient control valve 9 P
Mouth is sequentially connected, and the CF mouths of pressure-gradient control valve 9 are connected through check valve 7 with the P mouths for turning to steering gear 14 in circuit 34, the EF of pressure-gradient control valve 9
Mouth is connected with multi-way valve 27 in performance loop 35；The oil outlet of check valve 7 passes through an overflow valve respectively with the EF mouths of pressure-gradient control valve 9
Connect the oil return opening of fuel tank 2；Containing there are one four position and four-way reversing valves 24 of control boom cylinder action in the multi-way valve 27
With three six-way transfer valves 26 of a control dipper motion；
In the driving system, running motor controller 33, running motor 32 and transmission system 31 are sequentially connected；
The work drive motor controller 4 and running motor controller 33 are connect with 1 signal of entire car controller respectively；
The detection feedback unit is passed by speed probe 13, the steering pressure being connect respectively with 1 signal of entire car controller
Sensor 10, operating pressure sensor 30, swing arm handle displacement sensor 25 and scraper bowl handle displacement sensor 28 form；Institute
It states speed probe 13 to install on the steering wheel for being connected to and controlling steering gear 14, with the rotating speed of detection direction disk；The steering pressure
Force snesor 10 installs the oil outlet for being connected to the check valve 7, and the pressure in circuit 34 is turned to detection；The operating pressure
The installation of sensor 30 is connected at the EF mouths of pressure-gradient control valve 9, to detect the pressure of performance loop 35；The swing arm handle displacement sensing
Device 25 is installed at the control handle for four position and four-way reversing valves 24 for being connected to control boom cylinder action, to detect swing arm control
The displacement of handle；The scraper bowl handle displacement sensor 28, which is installed, is connected to three six that control bucket cylinder 23 acts logical commutations
At the control handle of valve 26, to detect the displacement that scraper bowl controls handle.
The steering circuit 34 is limited by steering gear 14, the first overflow valve 11, the second overflow valve 15, accumulator 12, right turn
Position valve 16, left steering limit valve 17 or gate shuttle valve 18, left steering hydraulic cylinder 19 and right turn hydraulic cylinder 20 form；
The accumulator 12 is connected to the oil outlet of check valve 7；
The steering gear 14 is to close the reactionless formula steering gear of core, the P mouths of steering gear 14 and the oil outlet mouth pipeline of constant displacement pump 6
Connection, and there are one check valve, L mouths and the left sides of steering gear 14 for installation on the pipeline that constant displacement pump 6 is connected to the P mouths of pressure-gradient control valve 9
The oil inlet piping connection of limiting steering valve 17, the oil outlet of left steering limit valve 17 have bar with left steering hydraulic cylinder 19 respectively
The rodless cavity piping connection of chamber and right turn hydraulic cylinder 20；The oil inlet pipeline of the R mouths and right turn limit valve 16 of steering gear 14
Connection, the oil outlet of right turn limit valve 16 have with the rodless cavity of left steering hydraulic cylinder 19 and right turn hydraulic cylinder 20 respectively
Rod cavity piping connection；Described or gate shuttle valve 18 both ends oil inlet respectively with the oil outlet and right turn of left steering limit valve 17
The oil inlet piping connection of the oil outlet piping connection of limit valve 16 or the oil outlet of gate shuttle valve 18 and the second overflow valve 15,
The oil outlet of second overflow valve 15 is connected through the second filter 8 with fuel tank 2；The oil inlet and check valve of first overflow valve 11
7 oil outlet is connected, and the oil outlet of the first overflow valve 11 is connected through the second filter 8 with fuel tank 2；The T mouths of steering gear 14 are through
Tow filtrator 8 is connected with fuel tank 2.
The performance loop 35 is by multi-way valve 27, the first boom cylinder 21, the second boom cylinder 22 and bucket cylinder
23 compositions；
The multi-way valve 27 includes 24, three six-way transfer valves 26 of four position and four-way reversing valve and third overflow valve
29；Four position and four-way reversing valve 24 and three six-way transfer valves 26 are hand-operated direction valve；Three six-way transfer valves 26
P mouths and P1 mouthfuls respectively with the EF of pressure-gradient control valve 9 mouth piping connections, and in the EF of pressure-gradient control valve 9 mouths to three six-way transfer valves
The branch road of 26 P1 mouths connection is equipped with a check valve；The A mouths of three six-way transfer valves 26 are through a check valve and four
The P mouths of four-way reversing valve 24 are connected；The rod chamber piping connection of the A1 mouths and bucket cylinder 23 of three six-way transfer valves 26, three
The rodless cavity piping connection of the B mouths and bucket cylinder 23 of six-way transfer valve 26；The T mouths of three six-way transfer valves 26 are through the first mistake
Filter 3 is connected with fuel tank 2；The A mouths of four position and four-way reversing valve 24 and the rodless cavity of the first boom cylinder 21 and second are dynamic
The rodless cavity piping connection of arm hydraulic cylinder 22, the B mouths of four position and four-way reversing valves 24 and the rod chamber of the first boom cylinder 21 and
The rod chamber piping connection of second boom cylinder 22, the T mouths of four position and four-way reversing valves 24 are through first filter 3 and 2 phase of fuel tank
Even；The oil inlet of the third overflow valve 29 is connected with the EF of pressure-gradient control valve 9 mouths, and the oil outlet of third overflow valve 29 is through the first mistake
Filter 3 is connected with fuel tank 2.
The work drive motor 5 and running motor 32 are permanent magnet synchronous motor, are accurately controlled to rotational speed and torque with realizing.
Compared with prior art, the beneficial effects of the utility model are：
1, control system described in the utility model drives constant displacement pump using motor, cheap compared with variable system, and
The constant displacement pump of reliable operation can reach control effect identical with variable system to be reduced into simplify system structure
This, improves the reliability of system.
2, control system described in the utility model is utilized respectively motor and drives preferential steering hydraulic system and driving system, real
Show therebetween mechanically decoupled, has made driver that need not consider the matching relationship problem of pedal and operation handle aperture, to
Alleviate the operation fatigue level of driver.
3, control system described in the utility model drives constant displacement pump using motor, controls the rotating speed of constant displacement pump, into
And the output flow of hydraulic system is accurately controlled, and according to the practical need of driver including direction disk rotating speed and handle aperture
Ask the output flow of control hydraulic system, pedal aperture and the operation handle aperture for effectively preventing conventional load machine unmatched
Problem and hydraulic system idling work state effectively reduce restriction loss, spill losses and middle position the off-load loss of system.
Description of the drawings
Fig. 1 is a kind of structural schematic diagram of electric drive loading machine electronic-hydraulic complex control system described in the utility model；
Fig. 2 is a kind of control process logical box of electric drive loading machine electronic-hydraulic complex control system described in the utility model
Figure.
In figure：
1- entire car controller 2- fuel tank 3- first filter 4- work drive motor controllers
5- work drive motor 6- constant displacement pump 7- check valves the second filters of 8-
9- pressure-gradient control valve 10- steering pressure sensor 11- the first overflow valve 12- accumulators
13- speed probe 14- steering gears 15- the second overflow valve 16- right turn limit valves
17- left steering limit valve 18- or gate shuttle valve 19- left steering hydraulic cylinder 20- right turn hydraulic cylinders
Tetra- position and four-way reversing valves of 21- the first boom cylinder 22- the second boom cylinder 23- bucket cylinders 24-
Tri- six-way transfer valve 27- multi-way valve 28- scraper bowl handle displacements of 25- swing arm handle displacement sensors 26-
Sensor
29- third overflow valve 30- operating pressure sensor 31- transmission system 32- running motors
33- running motor controllers 34- turns to circuit 35- performance loops.
Specific implementation mode
For the technical solution of the utility model and its caused advantageous effect is expanded on further, in conjunction with Figure of description,
Specific embodiment of the present utility model is as follows：
As shown in Figure 1, the utility model provides a kind of electric drive loading machine electronic-hydraulic complex control system, the control system
System is made of entire car controller, preferential steering hydraulic system, driving system and detection feedback unit.
The preferential steering hydraulic system includes：It is work drive motor controller 4, work drive motor 5, fuel tank 2, constant displacement pump 6, unidirectional
Valve 7, first filter 3, the second filter 8, pressure-gradient control valve 9 and steering circuit 34 and performance loop 35.
The signal output end of the signal receiving end and entire car controller 1 of the work drive motor controller 4 is connected by CAN bus
It connects；The output end of the work drive motor controller 4 is connect with work drive motor 5 by forceful electric power conducting wire and weakness signal wire, the work
Make electric machine controller 4 and receive the control instruction of entire car controller 1, and then the output power of work drive motor 5 is controlled；It is described
Work drive motor 5 is permanent magnet synchronous motor, the input shaft mechanical that the output shaft of the work drive motor 5 passes through shaft coupling and constant displacement pump 6
Connection, the oil inlet of the constant displacement pump 6 and 2 piping connection of fuel tank, the oil outlet of the constant displacement pump 6 and the pressure-gradient control valve 9 into
P mouthfuls of piping connections of hydraulic fluid port, and by a check valve, which is from fixed for installation between the P of constant displacement pump 6 and pressure-gradient control valve 9 mouths
The amount 6 P mouth one-way conductions to pressure-gradient control valve 9 of pump；The CF mouths of the pressure-gradient control valve 9 and the P mouth pipelines for turning to steering gear 14 in circuit 34
Connection, and check valve 7, the check valve are installed on the connecting line between the CF of pressure-gradient control valve 9 mouths and the P mouths of steering gear 14
7 is from the CF mouths of pressure-gradient control valve 9 to the P of steering gear 14 mouth one-way conductions；The EF mouths of the pressure-gradient control valve 9 respectively in performance loop 35
The P mouths and P1 mouthfuls of piping connections of three six-way transfer valves 26；The first filter 3 and the second filter 8 are separately mounted to oil
At two oil return openings of case 2.
The steering circuit 34 is limited by steering gear 14, the first overflow valve 11, the second overflow valve 15, accumulator 12, right turn
Position valve 16, left steering limit valve 17 or gate shuttle valve 18, left steering hydraulic cylinder 19 and right turn hydraulic cylinder 20 form.Described
It turns in circuit 34, the accumulator 12 installs the oil outlet for being connected to check valve 7；The steering gear 14 is reactionless to close core
Formula steering gear；The oil inlet piping connection of the L mouths and left steering limit valve 17 of steering gear 14, left steering limit valve 17 it is fuel-displaced
The mouth rodless cavity piping connection with the rod chamber of left steering hydraulic cylinder 19 and right turn hydraulic cylinder 20 respectively；The R mouths of steering gear 14
With the oil inlet piping connection of right turn limit valve 16, the oil outlet of right turn limit valve 16 respectively with left steering hydraulic cylinder 19
The rod chamber piping connection of rodless cavity and right turn hydraulic cylinder 20；Described or gate shuttle valve 18 both ends oil inlet respectively with left-hand rotation
To the oil outlet and the oil outlet piping connection of right turn limit valve 16 or the oil outlet and of gate shuttle valve 18 of limit valve 17
The oil outlet of the oil inlet piping connection of two overflow valves 15, the second overflow valve 15 is connected through the second filter 8 with fuel tank 2；It is described
The oil inlet of first overflow valve 11 is connected with the oil outlet of check valve 7, the oil outlet of the first overflow valve 11 through the second filter 8 with
Fuel tank 2 is connected；The T mouths of steering gear 14 are connected through the second filter 8 with fuel tank 2.
The performance loop 35 is by multi-way valve 27, the first boom cylinder 21, the second boom cylinder 22 and bucket cylinder
23 compositions.In the performance loop 35, the multi-way valve 27 includes that four position and four-way reversing valve 24, one three six is logical
Reversal valve 26 and third overflow valve 29；Four position and four-way reversing valve 24 and three six-way transfer valves 26 are hand-operated direction valve；
As previously mentioned, the P mouths of three six-way transfer valves 26 and P1 mouthfuls respectively with the EF of pressure-gradient control valve 9 mouth piping connections, and excellent
The branch road that the EF mouths of first valve 9 are connect with the P1 of three six-way transfer valves 26 mouths is equipped with a check valve, which serves as reasons
P1 mouth one-way conduction of the EF mouths of pressure-gradient control valve 9 to three six-way transfer valves 26；The A mouths of three six-way transfer valves 26 are through a list
It is connected to valve with the P mouths of four position and four-way reversing valves 24, and the check valve is from the A of three six-way transfer valves 26 mouths to four four
The P mouth one-way conductions of logical reversal valve 24；The rod chamber piping connection of the A1 mouths and bucket cylinder 23 of three six-way transfer valves 26, three
The rodless cavity piping connection of the B mouths and bucket cylinder 23 of position six-way transfer valve 26；The T mouths of three six-way transfer valves 26 are through the first mistake
Filter 3 is connected with fuel tank 2；The A mouths of four position and four-way reversing valve 24 and the rodless cavity of the first boom cylinder 21 and second are dynamic
The rodless cavity piping connection of arm hydraulic cylinder 22, the B mouths of four position and four-way reversing valves 24 and the rod chamber of the first boom cylinder 21 and
The rod chamber piping connection of second boom cylinder 22, the T mouths of four position and four-way reversing valves 24 are through first filter 3 and 2 phase of fuel tank
Even；The oil inlet of the third overflow valve 29 is connected with the EF of pressure-gradient control valve 9 mouths, and the oil outlet of third overflow valve 29 is through the first filtering
Device 3 is connected with fuel tank 2.
The driving system includes：Running motor controller 33, running motor 32 and transmission system 31.The running motor
The signal receiving end of controller 33 is connect with the signal output end of entire car controller 1 by CAN bus；The running motor control
The output end of device 33 is connect with running motor 32 by forceful electric power conducting wire and weakness signal wire, and the running motor controller 33 receives
The control instruction of entire car controller 1, and then the output power of running motor 32 is controlled；The running motor 32 is permanent magnetism
Synchronous motor；The output shaft of the running motor 32 is mechanically connected with transmission system 31.
The detection feedback unit includes speed probe 13, steering pressure sensor 10, operating pressure sensor 30, moves
Arm handle displacement sensor 25 and scraper bowl handle displacement sensor 28.The installation of the speed probe 13 is connected to control and turns to
On the steering wheel of device 14, with the rotating speed of detection direction disk, the speed probe 13 is connect with 1 signal of entire car controller, with to
Entire car controller 1 sends the steering wheel tach signal detected；The installation of steering pressure sensor 10 is connected to described unidirectional
The oil outlet of valve 7, the pressure in circuit 34 is turned to detection, and the steering pressure sensor 10 connects with 1 signal of entire car controller
It connects, to send the steering circuit pressure signal detected to entire car controller 1；The installation of operating pressure sensor 30 is connected to preferential
At the EF mouths of valve 9, to detect the pressure of performance loop 35, the operating pressure sensor 30 connects with 1 signal of entire car controller
It connects, to send the performance loop pressure signal detected to entire car controller 1；The swing arm handle displacement sensor 25 is installed
It is connected at the control handle of four position and four-way reversing valves 24 of control boom cylinder action, to detect the position that swing arm controls handle
It moves, the swing arm handle displacement sensor 25 is connect with 1 signal of entire car controller, with what is detected to the transmission of entire car controller 1
Swing arm controls handle displacement signal；The scraper bowl handle displacement sensor 28, which is installed, is connected to what control bucket cylinder 23 acted
At the control handle of three six-way transfer valves 26, to detect the displacement that scraper bowl controls handle, the scraper bowl handle displacement sensor
28 connect with 1 signal of entire car controller, and handle displacement signal is controlled to send the scraper bowl detected to entire car controller 1.
The course of work of electric drive loading machine electronic-hydraulic complex control system described in the utility model is：
The gear signal of the reception driver's input of entire car controller 1, accelerator pedal signal, steering wheel tach signal, swing arm
The pressure signal of the displacement signal and the steering circuit and performance loop that detect of handle and scraper bowl handle, through analyzing processing
Afterwards, respectively to work drive motor controller 4 and the output control signal of running motor controller 33, and then work drive motor 5 and row are controlled
The output power outward of motor 32 is sailed, realizes and drives preferential steering hydraulic system and driving system work.
Wherein：
Accelerator pedal signal value is V_APS, is K with running motor torque coefficient of correspondence, and K is variable；
Work drive motor rotating speed is N_pm1, and running motor torque is T_pm2；The steering wheel that speed probe 13 detects turns
Speed value is N_zx, is K1 with work drive motor rotating speed coefficient of correspondence, and K1 is constant；
The pressure value in the steering circuit 34 that steering pressure sensor 10 detects is P1, sets the first overflow valve 11 and second
The oil pressure relief of overflow valve 15 is P1_max, sets the pressure threshold for turning to circuit 34 as P_zx, and 0≤P_zx<P1_max；
The pressure value for the performance loop 35 that operating pressure sensor 30 detects is P2, the overflow of setting third overflow valve 29
Pressure is P2_max, sets the pressure threshold of performance loop 35 as P_gz, and 0≤P_gz<P2_max；
The swing arm handle displacement value that swing arm handle displacement sensor 26 detects is S_zx, scraper bowl handle displacement sensor 28
The scraper bowl handle displacement value detected is S_gz, is K2 with work drive motor rotating speed coefficient of correspondence, and K2 is constant.
As shown in Fig. 2, specific work process is as follows：
Control to running motor 32：
Entire car controller 1 controls running motor 32 after receiving accelerator pedal signal, 32 basis of running motor
Demand output torque be：T_pm2=V_APS × K；
Control to work drive motor 5：
Entire car controller 1 is in the displacement signal for receiving steering wheel tach signal, swing arm handle and scraper bowl handle and turns
After to the pressure signal of circuit and performance loop, the rotating speed of work drive motor 5 is controlled according to designed control method.Work
The rotating speed control entirety for making motor 5 is divided into both of which：General mode and energy saver mode.Under general mode, 5 rotating speed of work drive motor
Normal response operator demand；Under energy saver mode, in conjunction with rotating speed of the pressure value to work drive motor 5 for turning to circuit and performance loop
It is limited.The pressure value for turning to circuit that the switching of described two patterns will be detected according to steering pressure sensor 10, with
And the pressure value of performance loop that operating pressure sensor 30 detects is judged.Wherein, swing arm and scraper bowl are referred to as work
Device.
When equipment is failure to actuate, when loading machine steering, i.e.,：S_zx+S_gz=0, N_zx>When 0, if steering pressure senses
What device 10 detected turns to the pressure threshold that circuit pressure value is less than or equal to the steering circuit of setting, i.e.,：P1≤P_zx, then work
Make motor 5 and be operated in general mode, at this point, the output rotating speed of work drive motor 5 is：
N_pm1=N_zx × K1；
When equipment is failure to actuate, when loading machine steering, i.e.,：S_zx+S_gz=0, N_zx>When 0, if steering pressure senses
What device 10 detected turns to the pressure threshold that circuit pressure value is more than the steering circuit of setting, i.e.,：P1>P_zx, then work drive motor
5 are operated in energy saver mode, and control system limits the rotating speed of work drive motor 5, and the output rotating speed of work drive motor 5 is：
N_pm1=N_zx × K1 ×s [1-(P1-P_zx)/(P1_max-P_zx)].
When equipment is failure to actuate, if loading machine does not turn to, then work drive motor 5 does not export.
When equipment acts, if the steering circuit pressure value that steering pressure sensor 10 detects is less than or equal to setting
Steering circuit maximum pressure value (i.e.：The oil pressure relief of first overflow valve 11 and the second overflow valve 15), operating pressure sensing
The performance loop pressure value that device 30 detects is less than or equal to the pressure threshold of the performance loop of setting, i.e.,：P1≤P1_max, P2
When≤P_gz, work drive motor 5 is operated in general mode, the demand of normal response driver, at this point, work drive motor exports rotating speed
For：
N_pm1=K2 × (S_zx+S_gz)+N_zx × K1.
When equipment acts, if the steering circuit pressure value that steering pressure sensor 10 detects is less than or equal to setting
Steering circuit pressure threshold, the performance loop pressure value that operating pressure sensor 30 detects be more than setting performance loop
Pressure threshold, i.e.,：P1≤P_zx, P2>When P_gz, work drive motor 5 is operated in energy saver mode, and control system turns work drive motor
Speed is limited, and work drive motor output rotating speed is：
N_pm1=N_zx × K1+K2 × (S_zx+S_gz) × [1-(P2-P_gz)/(P2_max-P_gz)].
When equipment acts, if the circuit pressure value that turns to that steering pressure sensor 10 detects is more than turning for setting
To the pressure threshold in circuit, the performance loop pressure value that operating pressure sensor 30 detects is more than the pressure of the performance loop of setting
Force threshold, i.e.,：P1>P_zx, P2>When P_gz, work drive motor 5 is operated in energy saver mode, control system to work drive motor rotating speed into
Row limitation, work drive motor output rotating speed are：
N_pm1=N_zx × K1 ×s [1-(P1-P_zx)/(P1_max-P_zx)]+K2×(S_zx+S_gz)×[1-(P2-
P_gz) /(P2_max-P_gz)]。
In conclusion entire car controller 1 according to the vehicle signal received, controls work drive motor 5 and running motor 32 is defeated
The case where going out is as shown in following table one：
Table one
Claims (4)
1. a kind of electric drive loading machine electronic-hydraulic complex control system, it is characterised in that：
The control system is made of entire car controller, preferential steering hydraulic system, driving system and detection feedback unit；
In the preferential steering hydraulic system, work drive motor controller (4), work drive motor (5), constant displacement pump (6) and pressure-gradient control valve (9)
P mouths be sequentially connected, the CF mouths of pressure-gradient control valve (9) are connected through check valve (7) with the P mouths for turning to steering gear (14) in circuit (34),
The EF mouths of pressure-gradient control valve (9) are connected with multi-way valve (27) in performance loop (35)；The oil outlet of check valve (7) and pressure-gradient control valve (9)
The EF mouthfuls of oil return openings for connecting fuel tank (2) by an overflow valve respectively；Containing there are one control swing arm liquid in the multi-way valve (27)
Three six-way transfer valves (26) of four position and four-way reversing valves (24) of cylinder pressure action and a control dipper motion；
In the driving system, running motor controller (33), running motor (32) and transmission system (31) are sequentially connected；
The work drive motor controller (4) and running motor controller (33) are connect with entire car controller (1) signal respectively；
The detection feedback unit is passed by speed probe (13), the steering pressure being connect respectively with entire car controller (1) signal
Sensor (10), operating pressure sensor (30), swing arm handle displacement sensor (25) and scraper bowl handle displacement sensor (28)
Composition；Speed probe (13) installation is connected on the steering wheel of control steering gear (14), with the rotating speed of detection direction disk；
Steering pressure sensor (10) installation is connected to the oil outlet of the check valve (7), is turned to circuit (34) with detection
Pressure；Operating pressure sensor (30) installation is connected at the EF mouths of pressure-gradient control valve (9), to detect the pressure of performance loop (35)
Power；Swing arm handle displacement sensor (25) installation is connected to four position and four-way reversing valves (24) of control boom cylinder action
Control handle at, with detect swing arm control handle displacement；Scraper bowl handle displacement sensor (28) installation is connected to control
At the control handle of three six-way transfer valves (26) of bucket cylinder (23) action processed, to detect the displacement that scraper bowl controls handle.
2. a kind of electric drive loading machine electronic-hydraulic complex control system as described in claim 1, it is characterised in that：
The steering circuit (34) is by steering gear (14), the first overflow valve (11), the second overflow valve (15), accumulator (12), the right side
Limiting steering valve (16), left steering limit valve (17) or gate shuttle valve (18), left steering hydraulic cylinder (19) and right turn hydraulic cylinder
(20) it forms；
The accumulator (12) is connected to the oil outlet of check valve (7)；
The steering gear (14) is to close the reactionless formula steering gear of core, the P mouths of steering gear (14) and the oil outlet mouth pipe of constant displacement pump (6)
Road connects, and is installed there are one check valve on the pipeline that constant displacement pump (6) is connected to the P mouths of pressure-gradient control valve (9), steering gear (14)
L mouthfuls with the oil inlet piping connection of left steering limit valve (17), the oil outlet of left steering limit valve (17) respectively with left steering liquid
The rodless cavity piping connection of the rod chamber and right turn hydraulic cylinder (20) of cylinder pressure (19)；The R mouths of steering gear (14) are limited with right turn
The oil inlet piping connection of position valve (16), the oil outlet of right turn limit valve (16) is respectively with left steering hydraulic cylinder (19) without bar
The rod chamber piping connection of chamber and right turn hydraulic cylinder (20)；Described or gate shuttle valve (18) both ends oil inlet respectively with left-hand rotation
To the oil outlet and the oil outlet piping connection of right turn limit valve (16) or the oil outlet of gate shuttle valve (18) of limit valve (17)
With the oil inlet piping connection of the second overflow valve (15), the oil outlet of the second overflow valve (15) is through the second filter (8) and fuel tank
(2) it is connected；The oil inlet of first overflow valve (11) is connected with the oil outlet of check valve (7), and the first overflow valve (11) go out
Hydraulic fluid port is connected through the second filter (8) with fuel tank (2)；The T mouths of steering gear (14) are connected through the second filter (8) with fuel tank (2).
3. a kind of electric drive loading machine electronic-hydraulic complex control system as described in claim 1, it is characterised in that：
The performance loop (35) is by multi-way valve (27), the first boom cylinder (21), the second boom cylinder (22) and scraper bowl
Oil cylinder (23) forms；
The multi-way valve (27) includes four position and four-way reversing valve (24), three six-way transfer valves (26) and third overflow
Valve (29)；Four position and four-way reversing valve (24) and three six-way transfer valves (26) are hand-operated direction valve；Described three six logical
The P mouths of reversal valve (26) and P1 mouthfuls respectively with the EF mouth piping connections of pressure-gradient control valve (9), and in the EF mouths of pressure-gradient control valve (9) to three
The branch road of the P1 mouths connection of position six-way transfer valve (26) is equipped with a check valve；The A mouths warp of three six-way transfer valves (26)
One check valve is connected with the P mouths of four position and four-way reversing valves (24)；The A1 mouths and bucket cylinder of three six-way transfer valves (26)
(23) rod chamber piping connection, the rodless cavity piping connection of the B mouths and bucket cylinder (23) of three six-way transfer valves (26)；Three
The T mouths of position six-way transfer valve (26) are connected through first filter (3) with fuel tank (2)；The A mouths of four position and four-way reversing valve (24)
With the rodless cavity piping connection of the rodless cavity and the second boom cylinder (22) of the first boom cylinder (21), four four-way commutations
The rod chamber piping connection of the B mouths of valve (24) and the rod chamber and the second boom cylinder (22) of the first boom cylinder (21),
The T mouths of four position and four-way reversing valves (24) are connected through first filter (3) with fuel tank (2)；The oil inlet of the third overflow valve (29)
Mouth is connected with the EF mouths of pressure-gradient control valve (9), and the oil outlet of third overflow valve (29) is connected through first filter (3) with fuel tank (2).
4. a kind of electric drive loading machine electronic-hydraulic complex control system as described in claim 1, it is characterised in that：
The work drive motor (5) and running motor (32) are permanent magnet synchronous motor, are accurately controlled to rotational speed and torque with realizing.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201820264811.6U CN208009522U (en) | 2018-02-23 | 2018-02-23 | A kind of electric drive loading machine electronic-hydraulic complex control system |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201820264811.6U CN208009522U (en) | 2018-02-23 | 2018-02-23 | A kind of electric drive loading machine electronic-hydraulic complex control system |
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| CN208009522U true CN208009522U (en) | 2018-10-26 |
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| CN201820264811.6U Expired - Fee Related CN208009522U (en) | 2018-02-23 | 2018-02-23 | A kind of electric drive loading machine electronic-hydraulic complex control system |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108179780A (en) * | 2018-02-23 | 2018-06-19 | 吉林大学 | A kind of electric drive loading machine electronic-hydraulic complex control system and its control method |
| CN110777876A (en) * | 2019-12-03 | 2020-02-11 | 徐工集团工程机械股份有限公司科技分公司 | Work control system and method for electric loader |
| CN111156209A (en) * | 2020-02-28 | 2020-05-15 | 雷沃工程机械集团有限公司 | Loader hydraulic steering system and loader |
-
2018
- 2018-02-23 CN CN201820264811.6U patent/CN208009522U/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108179780A (en) * | 2018-02-23 | 2018-06-19 | 吉林大学 | A kind of electric drive loading machine electronic-hydraulic complex control system and its control method |
| CN110777876A (en) * | 2019-12-03 | 2020-02-11 | 徐工集团工程机械股份有限公司科技分公司 | Work control system and method for electric loader |
| CN111156209A (en) * | 2020-02-28 | 2020-05-15 | 雷沃工程机械集团有限公司 | Loader hydraulic steering system and loader |
| CN111156209B (en) * | 2020-02-28 | 2022-03-01 | 雷沃工程机械集团有限公司 | Loader hydraulic steering system and loader |
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