CN106813935A - A kind of loading device for simulating high-power level blower fan five degree of freedom load - Google Patents
A kind of loading device for simulating high-power level blower fan five degree of freedom load Download PDFInfo
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- 239000010720 hydraulic oil Substances 0.000 description 1
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- 239000007788 liquid Substances 0.000 description 1
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- G—PHYSICS
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- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
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Abstract
A kind of loading device for simulating high-power level blower fan five degree of freedom load, main shaft is rotationally coated with its loading disc, the left surface of loading disc applies the axially loaded cylinder group of left end, right flank applies the axially loaded cylinder group of right-hand member, outer ring surface applies radial loaded cylinder group, the axially loaded cylinder group of left end, the axially loaded cylinder group of right-hand member, radial loaded cylinder group is by being distributed in the left surface of loading disc, right flank, the hydraulic cylinder array of multiple point positions at equal intervals circumferentially of outer ring surface is constituted, the hydraulic cylinder array of each point position includes the 1 loading cylinder controlled by regular tap reversal valve of loading cylinder and N controlled by electro-hydraulic proportion reversing valve, by the loading access number of 1 regular tap reversal valve of aperture and N of computer control system control electro-hydraulic proportion reversing valve, just can be obtained in each point positionIn the range of any loading force.The problem that the cost of manufacture brought using large_sized hydraulic cylinder is increased, system response is slack-off, dynamic performance is deteriorated can be avoided.
Description
Technical field
The invention belongs to technical field of wind power generation, more particularly to a kind of high-power level blower fan five degree of freedom load of simulation
Loading device.
Background technology
Wind energy, with considerable reserves and cleaning recyclability, is opened it as a kind of emerging renewable green energy resource
Hair is using one of important channel for being solution energy crisis.The high mountain of awful weather is typically mounted at due to wind-driven generator, it is waste
Suburb and sea, blower fan driving-chain need to bear the load caused by unstable wind speed and direction for a long time, and thus cause gear
The failures such as case gear destruction, main shaft bearing failure.These problems have a strong impact on the life-span of unit, and increase the maintenance and repair of blower fan
Cost.The large-scale multiple degrees of freedom load charger for being capable of full simulation fan operation operating mode is thus built, can be raising blower fan
Reliability, the relevant design offer reference for improving blower fan stress, it is significant.
At present, the simulates blower fan load device of most domestic is all only limitted to simulate MxThe torque load in direction, it is impossible to complete
Comprehensive loading conditions of face simulates blower fan.How free notification number is for CN102636367B patents of invention give a kind of simulates blower fan
Spend the loading device of load, can effectively simulates blower fan comprehensive loading conditions.But for the blower fan of high-power level, suffered by it
Load all than larger, if according to the patent of invention（CN 102636367 B）The scheme given, it is necessary to custom-made it is large-scale plus
Cylinder is carried, corresponding hydraulic system will also be adjusted accordingly, need to such as use big flow proportioning valve and increase the hydraulic pump quantity of pumping plant,
This will increase loading device cost of manufacture, and, large-scale loading cylinder will cause the response of system slack-off, and the dynamic property of system becomes
Difference.
The content of the invention
In order to solve the above mentioned problem of prior art presence, the present invention provides a kind of high-power level blower fan five degree of freedom of simulation
The loading device of load, without using large-scale loading cylinder and the hydraulic system coordinated with large-scale loading cylinder, it is to avoid be fabricated to
This increase, make system respond it is slack-off, make dynamic performance be deteriorated problem.
In order to solve the above technical problems, the present invention is adopted the following technical scheme that：
A kind of loading device for simulating high-power level blower fan five degree of freedom load, including loading disc, pass through axle in the loading disc
Hold and be rotationally coated with main shaft, the left surface of the loading disc is applied with the axially loaded cylinder group of left end vertically, loading disc
Right flank is applied with the axially loaded cylinder group of right-hand member vertically, and the outer ring surface of loading disc is radially applied with radial loaded cylinder group, institute
State the axially loaded cylinder group of left end, the axially loaded cylinder group of right-hand member, radial loaded cylinder group and correspond to left surface, the right side by being distributed in loading disc
Side, the hydraulic cylinder array of multiple point positions at equal intervals circumferentially of outer ring surface are constituted, and each point position is disposed with a hydraulic pressure
Cylinder array, each hydraulic cylinder array is made up of N number of loading cylinder of N2, and it includes a loading controlled by electro-hydraulic proportion reversing valve
Cylinder and the N-1 loading cylinder for being controlled by regular tap reversal valve respectively, it is F to define each loading cylinder maximum output loading forcea, by
The loading force of the loading cylinder that electro-hydraulic proportion reversing valve is controlled is F0, the loading of each loading cylinder controlled by regular tap reversal valve
Power is Fi, then,, then total loading force of output of hydraulic cylinder array of each point position be, the aperture and N-1 of the electro-hydraulic proportion reversing valve are controlled by computer control system according to actual conditions
The loading access number of individual regular tap reversal valve, just can obtain in each point positionIn the range of any loading
Power；
The front end of all loading cylinders of the hydraulic cylinder array of each point position connects a sphere loading blocks jointly, by sphere loading blocks
It is pointed to the sphere plummer imposed load on loading disc.
The aperture and N-1 of the electro-hydraulic proportion reversing valve in hydraulic loaded loop is controlled commonly to open by computer control system
The loading access number of reversal valve is closed to control the loading force of the axially loaded cylinder of left end, the axially loaded cylinder of right-hand member, radial loaded cylinder,
Loading force passes to loading disc simultaneously, and then loading force is delivered on main shaft by bearing, and the combination by each loading force is complete
Into blower fan five degree of freedom load Fx, Fy, Fz, My, MzLoading.
Preferably, the left surface of the loading disc, right flank, outer ring surface have circumferentially been equidistantly spaced from eight points
Position, N number of loading cylinder of the hydraulic cylinder array of each point position is circumferentially equidistantly spaced from around respective Dian Wei centers.
Further, the loading device also includes the fixed mount affixed with the shell body, and N number of confession is provided with fixed mount
The chute that power block is slided is led, the rear end for leading power block opens up the groove for accommodating spring, and the front end of spring offsets with power block is led, spring
Rear end offsets with the piston rod of loading cylinder, and the position of N number of chute is corresponding with N number of loading cylinder in fixed mount, before each leads power block
End contradicts with the sphere loading blocks and is connected；
Then, piston rod of each loading cylinder by spring and is led power block loading force is delivered into sphere loading blocks, is finally led to
Sphere loading blocks are crossed the total loading force of the output of hydraulic cylinder array is applied on loading disc with the cooperation of sphere plummer.
Further, the hydraulic loaded loop of each point position is included to the loading oil supply cylinder of electro-hydraulic proportion reversing valve control
Second hydraulic circuit of the first hydraulic circuit and the loading oil supply cylinder to the control of each regular tap reversal valve, described first
Hydraulic circuit includes fuel tank, pump, high pressure filter, check valve, electro-hydraulic proportion reversing valve, hydraulic lock, loading cylinder, oil return filter
Device, thermoregulator, the outlet of the high pressure filter are connected with overflow valve, the inlet and outlet of the electro-hydraulic proportion reversing valve
Be connected with limited pressure level pressure difference import pressure-reducing pressure compensator, the entrance of the electro-hydraulic proportion reversing valve be also associated with pressure after
Electrical equipment, when oil pressure is too high pressure switch action warning system is alarmed, the electro-hydraulic proportion reversing valve be comprising loading with
The three position four-way directional control valve of unloading condition, the in-line connection temperature and pressure transmitter of the loading cylinder, loads the loading of cylinder
By temperature and pressure transmitter detection temperature and pressure to obtain, its testing result feeds back to the computer control system to power；
Second hydraulic circuit includes fuel tank, pump, high pressure filter, check valve, regular tap reversal valve, hydraulic lock, loading
Cylinder return filter, thermoregulator, the regular tap reversal valve is to be commutated with the 3-position 4-way of unloading condition comprising loading
Valve；
Two hydraulic control one-way valves that the hydraulic lock is connected by hydraulic control each other are constituted, when electro-hydraulic proportion reversing valve or regular tap are changed
During to valve dead electricity, hydraulic lock is in two equal lock-out states of hydraulic control one-way valve, it is possible to achieve the first hydraulic circuit and the second hydraulic pressure
The pressurize in loop.
The beneficial effects of the present invention are：1st, a kind of loading dress for simulating high-power level blower fan five degree of freedom load of the present invention
Put, can comprehensively, accurately and fast simulate the loading conditions of high-power blower, because each point position is replaced using multiple hydraulic cylinders
For the large-scale loading cylinder of script, the cost that the hydraulic system for being specifically manufactured large-scale loading cylinder and cooperation can be avoided to be brought increases
Problem, and it is slack-off and dynamic performance is deteriorated to respond system；
2nd, the hydraulic cylinder array of each point position of a kind of loading device for simulating high-power level blower fan five degree of freedom load of the present invention,
By using only an electro-hydraulic proportion reversing valve and needing the regular tap reversal valve of number just can to make the total of hydraulic cylinder array
Output loading force can reduce the usage quantity of electro-hydraulic proportion reversing valve in interior consecutive variations on a large scale, reduce manufacturing cost.
Brief description of the drawings
Fig. 1 is the coordinate diagram of blower fan six degree of freedom load of the invention.
Fig. 2 is drive mechanism, five degree of freedom load charger, total attachment structure figure of blower fan.
Fig. 3 is a kind of loading device embodiment for simulating high-power level blower fan five degree of freedom load of the present invention along spindle shaft
To sectional view.
Fig. 4 is the sectional view in Fig. 3 along main axis cross section.
Fig. 5 is the loading structure figure of the hydraulic cylinder array of each point position of the loading disc of the embodiment of the present invention.
Fig. 6 is the structure chart in the hydraulic loaded loop of each point position of the loading disc of the embodiment of the present invention.
Specific embodiment
In order to make the purpose , technical scheme and advantage of the present invention be clearer, it is right below in conjunction with drawings and Examples
The present invention is further elaborated.It should be appreciated that the specific embodiments described herein are merely illustrative of the present invention, and
It is not construed as limiting the invention.
Conversely, the present invention covers any replacement, modification, equivalent method and scheme made according to marrow of the present invention.Enter one
Step is detailed to describe some specific detail portions in examples below to make the public have a better understanding the present invention
Point, these specific detail sections are not limiting upon protection scope of the present invention.
Reference picture 1-6：A kind of loading device for simulating high-power level blower fan five degree of freedom load, including in shell body
Loading disc 2.3, main shaft 2.7 is rotationally coated with by bearing in the loading disc 2.3, the axially loaded cylinder group of left end is passed through
Shell body is applied to the left surface of the loading disc 2.3 vertically, and the axially loaded cylinder group of right-hand member applies vertically through shell body
In the right flank of loading disc 2.3, radial loaded cylinder group is radially applied to the outer ring surface of loading disc 2.3 through shell body, described
The axially loaded cylinder group of left end, the axially loaded cylinder group of right-hand member, radial loaded cylinder group correspondence by be distributed in loading disc 2.3 left surface,
Right flank, the hydraulic cylinder array 2.1 of eight points position at equal intervals circumferentially of outer ring surface are constituted, and each point position is disposed with one
Hydraulic cylinder array 2.1, in the present embodiment, each hydraulic cylinder array 2.1 is made up of N number of loading cylinder 5.1 of N2, this N number of loading cylinder
5.1 are circumferentially equidistantly spaced from around respective Dian Wei centers, and it includes a He of loading cylinder 5.1 controlled by electro-hydraulic proportion reversing valve
The N-1 loading cylinder 5.1 for being controlled by regular tap reversal valve respectively, it is F to define each loading cylinder 5.1 maximum output loading forcea,
The loading force of the loading cylinder 5.1 controlled by electro-hydraulic proportion reversing valve is F0, each loading cylinder controlled by regular tap reversal valve
5.1 loading force is Fi, then,Represent interval,,Set is represented, is represented common
Switch reversal valve control loading cylinder loading force be only 0 or, the then output of the hydraulic cylinder array 2.1 of each point position
Always loading force is, the electro-hydraulic proportion reversing valve is controlled by computer control system according to actual conditions
Aperture and the N-1 loading access number of regular tap reversal valve, just can each point position obtainScope
Interior any loading force.
The front end of all loading cylinders 5.1 of the hydraulic cylinder array 2.1 of each point position connects a sphere loading blocks 2.2, loading
There is a sphere plummer 2.4 coordinated with the sphere loading blocks 2.2, the hydraulic cylinder array 2.1 of each point position passes through on disk 2.3
Load is applied to sphere loading blocks 2.2 the sphere plummer 2.4 on loading disc 2.3；
Hydraulic loaded loop is controlled by computer control system（Including first hydraulic pressure controlled by electro-hydraulic proportion reversing valve
Loop and N-1 the second hydraulic circuit for being controlled by regular tap reversal valve respectively）Electro-hydraulic proportion reversing valve aperture and N-1
The loading access number of individual regular tap reversal valve, to control the axially loaded cylinder of left end, the axially loaded cylinder of right-hand member, radial loaded cylinder
Loading force, while loading force passes to loading disc 2.3, and then loading force is delivered on main shaft 2.7 by bearing, by each
The combination of loading force completes blower fan five degree of freedom load Fx, Fy, Fz, My, MzLoading.
Fig. 1 is the coordinate diagram of the blower fan six degree of freedom load of invention.Wherein coordinate system is defined as follows：X-axis is along main shaft square
To, downbeam is pointed to, Z axis are vertical with X-axis and Y-axis, and Y-axis is vertical with X-axis and Z axis, and X-axis, Y-axis, Z axis constitute right-handed scale (R.H.scale)
System.FxRepresent the loading force of X-axis positive direction, FyRepresent the loading force of Y-axis positive direction, FzRepresent the loading force of Z axis positive direction, My
Represent overturning moment, MzRepresent driftage moment of flexure, above-mentioned composition five degree of freedom load of the invention, additionally, MxRepresent drive mechanism band
The torque of the dynamic rotation of main shaft 2.7.
Fig. 2 is drive mechanism, five degree of freedom load charger, total attachment structure figure of blower fan.It is loading by test specimen 1
Power effective object, is fixed on the ground by base.Five degree of freedom load charger 2 passes through the axially loaded cylinder group of left end, a left side
Axially loaded cylinder group, radial loaded cylinder group are held to loading disc imposed load, and then by main shaft to by the imposed load of test specimen 1, respectively
Loading force combination is completed to by five free degree load F of test specimenx, Fy, Fz, My, MzLoading；Drive mechanism 4 passes through 3 pairs, shaft coupling
M is applied by test specimen 1xLoad, is rotated with drive shaft.
Fig. 3 is the structure chart of five degree of freedom load charger.The shell body includes being bolted the left housing of connection
Body 2.6 and right shell body 2.8, the affixed support frame 2.5 in lower end of the shell body, are fixedly connected on the loading cylinder 5.1 on shell body
To the imposed load of loading disc 2.3, and then apply to carry by 2. 9 main shaft of bearing 2.7 connected between loading disc 2.3 and main shaft 2.7
Lotus.Shell body is used for the loading cylinder 5.1 for supporting to fix each point position.
In the present embodiment, the bearing 2.9 for being connected between the loading disc 2.3 and main shaft 2.7 is pushed away for that can bear axial direction
The thrust bearing of power.
Fig. 5 is the loading structure figure of the hydraulic cylinder array of each point position of loading disc.Five degree of freedom load charger is also wrapped
Include with the shell body by the affixed fixed mount 2.12 of screw 2.11, be provided with fixed mount 2.12 and N number of slided for leading power block 2.13
Capable chute, lead power block 2.13 rear end open up accommodate spring 2.10 groove, the front end of spring 2.10 with lead the phase of power block 2.13
Support, rear end and the piston rod of loading cylinder of spring 2.10 offset, the position of N number of chute and N number of loading cylinder 5.1 in fixed mount 2.12
Correspondence, each front end for leading power block 2.13 connects a sphere loading blocks 2.2 jointly, and each leads power block 2.13 and sphere loading blocks
2.2 connect for conflict；
Then, loading force is delivered to sphere loading by the piston rod of each loading cylinder 5.1 by spring 2.9 with power block 2.13 is led
Block 2.2, finally by the cooperation of sphere loading blocks 2.2 and sphere plummer 2.4 by the total loading force of the output of hydraulic cylinder array 2.1
It is applied on loading disc 2.3.Spring 2.10 plays a part of to buffer and preloading, sphere loading blocks 2.2 and sphere plummer 2.4
Cooperation cause that the loading of hydraulic cylinder array 2.1 is more concentrated, and hydraulic pressure when overcoming the different loading cylinders of hydraulic cylinder array 2.1 to load
Difference of the point of resultant force of cylinder array 2.1 to main-shaft axis distance.
Fig. 6 is the structure chart in the hydraulic loaded loop of each point position of the loading disc of the embodiment of the present invention.The figure is with each point
The hydraulic cylinder array of position is illustrated comprising 4 loading cylinders, and a loading cylinder 5.1a is changed by electric-hydraulic proportion in this four loading cylinders
To valve control, its oil circuit is the first hydraulic circuit, and the other three loading cylinder is controlled by regular tap reversal valve respectively, and its oil circuit is
Second hydraulic circuit；
First hydraulic circuit includes fuel tank 100, pump 5.11, high pressure filter 5.8, check valve 5.7, electro-hydraulic proportion reversing valve
5.5th, hydraulic lock 5.3a, loading cylinder 5.1a, return filter 5.16, thermoregulator 5.15, the high pressure filter 5.8 go out
Mouth is connected with overflow valve 5.9, and the inlet and outlet of the electro-hydraulic proportion reversing valve 5.5 is connected with the difference import decompression of limited pressure level pressure
Type pressure compensator 5.4, its effect is to make the pressure difference of inlet and outlet constant so that the flow of electro-hydraulic proportion reversing valve 5.5 by
Its aperture determines that the entrance of the electro-hydraulic proportion reversing valve 5.5 is also associated with pressure switch 5.6, the electric-hydraulic proportion commutation
Valve 5.5 is three position four-way directional control valve, and the left position correspondence of the three position four-way directional control valve loads the loading of cylinder, and interposition is to disconnect,
The off-load of right position correspondence loading cylinder, the in-line connection temperature and pressure transmitter 5.2 of the loading cylinder 5.1a；
Second hydraulic circuit includes fuel tank 100, pump 5.11, high pressure filter 5.8, check valve 5.7, regular tap reversal valve
（5.17a、5.17b、5.17c）, hydraulic lock（5.3b、5.3c、5.3d）, loading cylinder（5.1b、5.1c、5.1d）, return filter
5.16th, thermoregulator 5.15, the regular tap reversal valve（5.17a、5.17b、5.17c）It is three position four-way directional control valve, should
The loading of the left position correspondence loading cylinder of three position four-way directional control valve, to disconnect, right position correspondence loads the off-load of cylinder to interposition.First
Fuel tank 100, pump 5.11 in hydraulic circuit and the second hydraulic circuit, high pressure filter 5.8, check valve 5.7, return filter
5.16th, thermoregulator 5.15 constitutes the two common main line.
The hydraulic lock（5.3a、5.3b、5.3c、5.3d）Two hydraulic control one-way valves connected by hydraulic control each other are constituted, when
During one of hydraulic control one-way valve oil-feed, the oil circuit control of another hydraulic control one-way valve obtains fluid makes valve port opening to return
Oil.
During loading, computer control system obtains the loading of each hydraulic cylinder array for putting position by load decomposition computation
Power, the power output of each loading cylinder of the size control hydraulic cylinder array according to loading force.Start motor 5.14, by shaft coupling
5.13 drive pump 5.11, and hydraulic oil is single by high pressure filter 5.8 after pump 5.11 pressurizes via oil absorption filter 5.12
To valve 5.7, main line feed system working solution force feed is formed.
It is F to define each loading cylinder maximum output loading forcea, the loading force of the loading cylinder controlled by electro-hydraulic proportion reversing valve
It is F0, the loading force of each loading cylinder controlled by regular tap reversal valve is Fi（i=1,2,3）, then,, then each point position hydraulic cylinder array the total loading force of output。
The loading force of the hydraulic cylinder array obtained by being calculated when computer control systemWhen, by electric-hydraulic proportion
The controlled loading cylinder 5.1a of reversal valve 5.5 is individually loaded, while loading cylinder 5.1b, loading cylinder 5.1c and loading cylinder 5.1d off-loads.Should
Under operating mode, in-line is：Oil absorption filter 5.12, pump 5.11, high pressure filter 5.8, check valve 5.7, electro-hydraulic proportion reversing valve
5.5 left positions, the left positions of hydraulic lock 5.3a load cylinder 5.1a rodless cavities.Oil return line is：Loading cylinder 5.1a rod chambers, hydraulic lock 5.3a
Right position, the left position of electro-hydraulic proportion reversing valve 5.5, return filter 5.16, thermoregulator 5.15, fuel tank 100.
When the loading force of the hydraulic cylinder array obtained by calculatingWhen, controlled by electro-hydraulic proportion reversing valve 5.5
Loading cylinder 5.1a, regular tap reversal valve 5.17a control loading cylinder 5.1b load jointly, while load cylinder 5.1c and loading
Cylinder 5.1d off-loads.Under the operating mode, in-line is：Oil absorption filter 5.12, pump 5.11, high pressure filter 5.8, check valve 5.7, then
Via the oil inlet passage of each branch road；Wherein loading cylinder 5.1a branch roads oil inlet passage be：The left position of electro-hydraulic proportion reversing valve 5.5,
The left positions of hydraulic lock 5.3a, load cylinder 5.1a rodless cavities；Wherein loading cylinder 5.1b branch roads oil inlet passage be：Regular tap reversal valve
The left positions of 5.17a, the left positions of hydraulic lock 5.3b load cylinder 5.1b rodless cavities.Oil return line is：Converged via the drainback passage of each branch road
Always, then by return filter 5.16, thermoregulator 5.15 returns to fuel tank 100；The oil return of wherein loading cylinder 5.1a branch roads is led to
Road is：Loading cylinder 5.1a rod chambers, the right positions of hydraulic lock 5.3a, the left position of electro-hydraulic proportion reversing valve 5.5；Wherein load cylinder 5.1b branch roads
Drainback passage be：Loading cylinder 5.1b rod chambers, the right positions of hydraulic lock 5.3b, the left positions of regular tap reversal valve 5.17a.
When the loading force of the hydraulic cylinder array obtained by calculatingWhen, controlled by electro-hydraulic proportion reversing valve 5.5
The loading cylinder 5.1a of system, loading cylinder 5.1b and regular tap reversal valve the 5.17b control of regular tap reversal valve 5.17a controls
The loading cylinder 5.1c of system is loaded jointly, while loading cylinder 5.1d off-loads.Under the operating mode, in-line is：Oil absorption filter 5.12, pump
5.11, high pressure filter 5.8, check valve 5.7, then via the oil inlet passage of each branch road；Wherein load entering for cylinder 5.1a branch roads
Oily passage is：The left position of electro-hydraulic proportion reversing valve 5.5, the left positions of hydraulic lock 5.3a load cylinder 5.1a rodless cavities；Wherein loading cylinder 5.1b
The oil inlet passage of branch road is：The left positions of regular tap reversal valve 5.17a, the left positions of hydraulic lock 5.3b load cylinder 5.1b rodless cavities；Wherein
Load cylinder 5.1c branch roads oil inlet passage be：The left positions of regular tap reversal valve 5.17b, the left positions of hydraulic lock 5.3c, loading cylinder 5.1c
Rodless cavity.Oil return line is：Drainback passage via each branch road collects, then by return filter 5.16, thermoregulator
5.15, return to fuel tank 100；Wherein loading cylinder 5.1a branch roads drainback passage be：Loading cylinder 5.1a rod chambers, hydraulic lock 5.3a is right
Position, the left position of electro-hydraulic proportion reversing valve 5.5；Wherein loading cylinder 5.1b branch roads drainback passage be：Loading cylinder 5.1b rod chambers, hydraulic pressure
The right positions of lock 5.3b, the left positions of regular tap reversal valve 5.17a；Wherein loading cylinder 5.1c branch roads drainback passage be：Loading cylinder 5.1c
Rod chamber, the right positions of hydraulic lock 5.3c, the left positions of regular tap reversal valve 5.17b.
When the loading force of the hydraulic cylinder array obtained by calculatingWhen, controlled by electro-hydraulic proportion reversing valve 5.5
The loading cylinder 5.1a of system, the loading cylinder 5.1b of regular tap reversal valve 5.17a controls, regular tap reversal valve 5.17b are controlled
The loading cylinder 5.1d of loading cylinder 5.1c and regular tap reversal valve 5.17c controls is loaded jointly.Under the operating mode, in-line is：
Oil absorption filter 5.12, pump 5.11, high pressure filter 5.8, check valve 5.7, then via the oil inlet passage of each branch road；Wherein plus
Carry cylinder 5.1a branch roads oil inlet passage be：The left position of electro-hydraulic proportion reversing valve 5.5, the left positions of hydraulic lock 5.3a, cylinder 5.1a is without bar for loading
Chamber；Wherein loading cylinder 5.1b branch roads oil inlet passage be：The left positions of regular tap reversal valve 5.17a, the left positions of hydraulic lock 5.3b, loading
Cylinder 5.1b rodless cavities；Wherein loading cylinder 5.1c branch roads oil inlet passage be：The left positions of regular tap reversal valve 5.17b, hydraulic lock
The left positions of 5.3c, load cylinder 5.1c rodless cavities；Wherein loading cylinder 5.1d branch roads oil inlet passage be：Regular tap reversal valve 5.17c
The left position of Zuo Wei, hydraulic lock 5.3d, loads cylinder 5.1d rodless cavities.Oil return line is：Drainback passage via each branch road collects, then passes through
Return filter 5.16 is crossed, thermoregulator 5.15 returns to fuel tank 100；Wherein loading cylinder 5.1a branch roads drainback passage be：Plus
Carry cylinder 5.1a rod chambers, the right positions of hydraulic lock 5.3a, the left position of electro-hydraulic proportion reversing valve 5.5；Wherein load the oil return of cylinder 5.1b branch roads
Passage is：Loading cylinder 5.1b rod chambers, the right positions of hydraulic lock 5.3b, the left positions of regular tap reversal valve 5.17a；Wherein loading cylinder 5.1c
The drainback passage of branch road is：Loading cylinder 5.1c rod chambers, the right positions of hydraulic lock 5.3c, the left positions of regular tap reversal valve 5.17b；Wherein
Load cylinder 5.1d branch roads drainback passage be：Loading cylinder 5.1d rod chambers, the right positions of hydraulic lock 5.3d, regular tap reversal valve
The left positions of 5.17c.
During off-load, electro-hydraulic proportion reversing valve 5.5 and regular tap reversal valve（5.17a、5.17b、5.17c）Right position work.
Under the operating mode, in-line is：Oil absorption filter 5.12, pump 5.11, high pressure filter 5.8, check valve 5.7, then via each branch
The oil inlet passage on road；Wherein loading cylinder 5.1a branch roads oil inlet passage be：The right position of electro-hydraulic proportion reversing valve 5.5, hydraulic lock 5.3a
Right position, loads cylinder 5.1a rod chambers；Wherein loading cylinder 5.1b branch roads oil inlet passage be：The right positions of regular tap reversal valve 5.17a,
The right positions of hydraulic lock 5.3b, load cylinder 5.1b rod chambers；Wherein loading cylinder 5.1c branch roads oil inlet passage be：Regular tap reversal valve
The right positions of 5.17b, the right positions of hydraulic lock 5.3c load cylinder 5.1c rod chambers；Wherein loading cylinder 5.1d branch roads oil inlet passage be：Commonly
The right positions of switch reversal valve 5.17c, the right positions of hydraulic lock 5.3d load cylinder 5.1d rod chambers.Oil return line is：Via returning for each branch road
Oily passage collects, then by return filter 5.16, thermoregulator 5.15 returns to fuel tank 100；Wherein load cylinder 5.1a branch roads
Drainback passage be：Loading cylinder 5.1a rodless cavities, the left positions of hydraulic lock 5.3a, the right position of electro-hydraulic proportion reversing valve 5.5；Wherein load cylinder
The drainback passage of 5.1b branch roads is：Loading cylinder 5.1b rodless cavities, the left positions of hydraulic lock 5.3b, the right positions of regular tap reversal valve 5.17a；
Wherein loading cylinder 5.1c branch roads drainback passage be：Loading cylinder 5.1c rodless cavities, the left positions of hydraulic lock 5.3c, regular tap reversal valve
The right positions of 5.17b；Wherein loading cylinder 5.1d branch roads drainback passage be：Loading cylinder 5.1d rodless cavities, the left positions of hydraulic lock 5.3d, commonly
The right positions of switch reversal valve 5.17c.
When electro-hydraulic proportion reversing valve 5.5, regular tap reversal valve（5.17a、5.17b、5.17c）During dead electricity, the two is in
Interposition is closed mode, and hydraulic lock is in the lock state, and then each branch road is by corresponding hydraulic lock（5.3a, 5.3b, 5.3c,
5.3d）Pressurize.
In loading procedure, the loading force for loading cylinder 5.1 is detected by temperature and pressure transmitter 5.2, and feeds back to computer
Control system, loading force program and the synchronized Coordinative Control are realized by industrial computer and software programming.The detection of pressure switch 5.6 system
System oil pressure, when oil pressure is too high, pressure switch 5.6 is acted, acoustooptic alarm system alarm, reminds staff to be overhauled.
As the loading cylinder quantity N of hydraulic cylinder array>During 4 or 2N3, operation principle is as above.Wherein there is 1 loading cylinder by electricity
Liquid proportional reversal valve is controlled, and remaining N-1 loading cylinder is controlled by regular tap reversal valve, and each puts the defeated of the hydraulic cylinder array of position
Going out total loading force is, control the aperture and N-1 of electro-hydraulic proportion reversing valve individual common according to actual conditions
The loading access number of reversal valve is switched, just be can obtainIn the range of any loading force.
These are only presently preferred embodiments of the present invention, be not intended to limit the invention, it is all it is of the invention spirit and
Any modification, equivalent and improvement for being made within principle etc., should be included within the scope of the present invention.
Claims (5)
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