CN106813935B - A loading device for simulating the five-degree-of-freedom load of a high-power fan - Google Patents
A loading device for simulating the five-degree-of-freedom load of a high-power fan Download PDFInfo
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- CN106813935B CN106813935B CN201611226874.4A CN201611226874A CN106813935B CN 106813935 B CN106813935 B CN 106813935B CN 201611226874 A CN201611226874 A CN 201611226874A CN 106813935 B CN106813935 B CN 106813935B
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
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- G—PHYSICS
- G01—MEASURING; TESTING
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Abstract
A kind of loading device for simulating high-power grade blower five degree of freedom load, main shaft is rotationally coated in its loading disc, the left side of loading disc applies the axially loaded cylinder group in left end, right side applies the axially loaded cylinder group of right end, outer ring surface applies radial loaded cylinder group, the axially loaded cylinder group in left end, the axially loaded cylinder group of right end, radial loaded cylinder group is by being distributed in the left side of loading disc, right side, the hydraulic cylinder array of multiple points at equal intervals circumferentially of outer ring surface is constituted, the hydraulic cylinder array of each point includes a load cylinder and the N-1 load cylinders controlled by regular tap reversal valve by electro-hydraulic proportion reversing valve control, by the aperture of computer control system control electro-hydraulic proportion reversing valve and the load access number of N-1 regular tap reversal valve, it can be obtained in each pointAny loading force in range.It can avoid responding the problem of slack-off, dynamic performance is deteriorated using the increase of large_sized hydraulic cylinder bring cost of manufacture, system.
Description
Technical field
It is the invention belongs to technical field of wind power generation, in particular to a kind of to simulate high-power grade blower five degree of freedom load
Loading device.
Background technique
Wind energy opens it with considerable reserves and cleaning reproducibility as a kind of emerging renewable green energy resource
Hair utilizes one of the important channel for being solution energy crisis.It is waste since wind-driven generator is typically mounted at the high mountain of awful weather
Suburb and sea, blower transmission chain needs load caused by bearing unstable wind speed and direction for a long time, and thus leads to gear
The failures such as case gear destruction, main shaft bearing failure.These problems seriously affect the service life of unit, and increase the maintenance and repair of blower
Cost.Thus the large-scale multiple degrees of freedom load charger of full simulation fan operation operating condition is capable of in construction, can be raising blower
Reliability, the relevant design for improving blower stress provide reference, are of great significance.
Currently, the simulates blower fan load device of most domestic is all only limitted to simulation MxThe torque load in direction, Wu Faquan
Comprehensive loading conditions of face simulates blower fan.Notification number is that how free give a kind of simulates blower fan for CN102636367B patent of invention
Spend the loading device of load, can effectively simulates blower fan comprehensive loading conditions.But it is directed to the blower of high-power grade, suffered by
Load is all bigger, if needing custom-made large size to add according to the scheme that the patent of invention (102636367 B of CN) is given
Cylinder is carried, corresponding hydraulic system will also adjust accordingly, if you need to using big flow proportioning valve and increase the hydraulic pump quantity of pumping plant,
This will increase loading device cost of manufacture, moreover, the response that large-scale load cylinder will lead to system is slack-off, the dynamic property of system becomes
Difference.
Summary of the invention
In order to solve the above problems existing in the present technology, the present invention provides a kind of high-power grade blower five degree of freedom of simulation
The loading device of load, the hydraulic system without large-scale load cylinder and with large-scale load cylinder cooperation, avoids and is fabricated to
This increase makes that system response is slack-off, the problem of making dynamic performance be deteriorated.
In order to solve the above technical problems, the present invention adopts the following technical scheme that:
A kind of loading device for simulating high-power grade blower five degree of freedom load, including loading disc lead in the loading disc
It crosses bearing and is rotationally coated with main shaft, the left side of the loading disc is axially disposed the axially loaded cylinder group in left end, load
The right side of disk is axially disposed the axially loaded cylinder group of right end, and the outer ring surface of loading disc has been disposed radially radial loaded cylinder
Group, the axially loaded cylinder group in the left end, the axially loaded cylinder group of right end, radial loaded cylinder group correspond to the left side by being distributed in loading disc
Face, right side, outer ring surface the hydraulic cylinder arrays of multiple points at equal intervals circumferentially constitute, each point is disposed with one
Hydraulic cylinder array, each hydraulic cylinder array are made of N number of load cylinder comprising a load controlled by electro-hydraulic proportion reversing valve
Cylinder and the N-1 load cylinders controlled respectively by regular tap reversal valve, defining each load cylinder maximum output loading force is Fa, by
The loading force of the load cylinder of electro-hydraulic proportion reversing valve control is F0, the load of the load cylinder each controlled by regular tap reversal valve
Power is Fi, then F0∈ [0, Fa], Fi∈ { 0, Fa, then the total loading force of output of the hydraulic cylinder array of each point isThe aperture and N-1 of the electro-hydraulic proportion reversing valve are controlled by computer control system according to the actual situation
The load access number of a regular tap reversal valve can obtain [0, N × F in each pointa] any loading force in range；
The front end of all load cylinders of the hydraulic cylinder array of each point connects a spherical surface loading blocks jointly, by spherical surface plus
It carries block and load is applied to the spherical surface plummer being located on loading disc.
The aperture of the electro-hydraulic proportion reversing valve in hydraulic loaded circuit is controlled by computer control system and N-1 are commonly opened
The load access number of reversal valve is closed to control the loading force of the axially loaded cylinder in left end, the axially loaded cylinder of right end, radial loaded cylinder,
Loading force passes to loading disc simultaneously, and then loading force is transmitted on main shaft by bearing, and the combination by each loading force is complete
At blower five degree of freedom load Fx, Fy, Fz, My, MzLoad.
Preferably, the left side of the loading disc, right side, outer ring surface have circumferentially been equidistantly spaced from eight points
Position, N number of load cylinder of the hydraulic cylinder array of each point are circumferentially equidistantly spaced from around respective point center.
Further, the loading device further includes the fixed frame affixed with the outer housing, is equipped with N number of confession in fixed frame
The sliding slot that power block slides 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 and the piston rod of load cylinder offset, and the position of N number of sliding slot is corresponding with N number of load cylinder in fixed frame, before each power of leading block
End contradicts with the spherical surface loading blocks and connects；
Then, the piston rod of each load cylinder, which passes through spring and leads power block, is transmitted to spherical surface loading blocks for loading force, most
The total loading force of the output of hydraulic cylinder array is applied on loading disc by the cooperation of spherical surface loading blocks and spherical surface plummer afterwards.
Further, the hydraulic loaded circuit of each point includes the load oil supply cylinder controlled to electro-hydraulic proportion reversing valve
Second hydraulic circuit of the first hydraulic circuit and the load oil supply cylinder controlled to 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, load 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 connected with pressure after
Electric appliance, when oil pressure is excessively high pressure switch movement so that alarm system is alarmed, the electro-hydraulic proportion reversing valve be comprising load with
The oil inlet pipe of the three position four-way directional control valve of unloading condition, the load cylinder connects temperature and pressure transmitter, loads the load of cylinder
Power detects temperature and pressure by temperature and pressure transmitter to obtain, and testing result feeds back to the computer control system；
Second hydraulic circuit include fuel tank, pump, high pressure filter, check valve, regular tap reversal valve, hydraulic lock,
Cylinder return filter, thermoregulator are loaded, the regular tap reversal valve is comprising loading the 3-position 4-way with unloading condition
Reversal valve；
The hydraulic lock is made of two hydraulic control one-way valves that hydraulic control each other connects, and when electro-hydraulic proportion reversing valve or is commonly opened
When closing reversal valve power loss, hydraulic lock is in two equal lock states of hydraulic control one-way valve, and the first hydraulic circuit and second may be implemented
The pressure maintaining of hydraulic circuit.
The beneficial effects of the present invention are: 1, the present invention a kind of load dress of simulating high-power grade blower five degree of freedom load
It sets, can comprehensively, accurately and fast simulate the loading conditions of high-power blower, since each point is replaced using multiple hydraulic cylinders
For the large-scale load cylinder of script, can avoid being specifically manufactured increased costs brought by the hydraulic system of large-scale load cylinder and cooperation
The problem of, and system response will not be made slack-off and dynamic performance is made to be deteriorated；
2, a kind of hydraulic cylinder of each point for the loading device for simulating high-power grade blower five degree of freedom load of the present invention
Array, by the way that an electro-hydraulic proportion reversing valve is used only and needs the regular tap reversal valve of number can be so that hydraulic cylinder array
Total output loading force it is a wide range of at one in consecutive variations, the usage quantity of electro-hydraulic proportion reversing valve can be reduced, reduce manufacture
Cost.
Detailed description of the invention
Fig. 1 is the coordinate diagram of blower six degree of freedom load of the invention.
Fig. 2 is driving mechanism, the overall connection structure diagram of five degree of freedom load charger, blower.
Fig. 3 is a kind of loading device embodiment for simulating high-power grade blower five degree of freedom load of the present invention along spindle shaft
To cross-sectional view.
Fig. 4 is the cross-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 of loading disc of the embodiment of the present invention.
Fig. 6 is the structure chart in the hydraulic loaded circuit of each point of loading disc of the embodiment of the present invention.
Specific embodiment
In order to make the objectives, technical solutions, and advantages of the present invention clearer, with reference to the accompanying drawings and embodiments, right
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.
On the contrary, the present invention cover it is any according to substitution made by marrow of the present invention, modify, equivalent method and scheme.Into one
Step is detailed to describe some specific detail portions in following examples 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.
Referring to Fig.1-6: a kind of loading device for simulating high-power grade blower five degree of freedom load, including be located in outer housing
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 in left end passes through
Outer housing is axially arranged on the left side of the loading disc 2.3, and it is axially disposed that the axially loaded cylinder group of right end passes through outer housing
In the right side of loading disc 2.3, radial loaded cylinder group passes through the outer ring surface that outer housing is arranged radially in loading disc 2.3, described
The corresponding left side by being distributed in loading disc 2.3 of the axially loaded cylinder group in left end, the axially loaded cylinder group of right end, radial loaded cylinder group,
Right side, outer ring surface the hydraulic cylinder arrays 2.1 of eight points at equal intervals circumferentially constitute, each point is disposed with one
Hydraulic cylinder array 2.1, in the present embodiment, each hydraulic cylinder array 2.1 is made of N number of load cylinder 5.1, this N number of load cylinder 5.1 around
Respective point center is circumferentially equidistantly spaced from comprising one by the load cylinder 5.1 of electro-hydraulic proportion reversing valve control and N-1
The load cylinder 5.1 controlled respectively by regular tap reversal valve, defining each 5.1 maximum output loading force of load cylinder is Fa, by electricity
The loading force of the load cylinder 5.1 of liquid proportional reversal valve control is F0, the load cylinder 5.1 that is each controlled by regular tap reversal valve
Loading force is Fi, then F0∈ [0, Fa], [] indicates section, Fi∈ { 0, Fa, { } indicates set, represents regular tap reversal valve control
The loading force of the load cylinder of system is only 0 or Fa, and then the total loading force of output of the hydraulic cylinder array 2.1 of each point isThe aperture and N-1 of the electro-hydraulic proportion reversing valve are controlled by computer control system according to the actual situation
The load access number of a regular tap reversal valve can obtain [0, N × F in each pointa] any loading force in range.
The front end of all load cylinders 5.1 of the hydraulic cylinder array 2.1 of each point connects a spherical surface loading blocks 2.2, load
Spherical surface plummer 2.4 on disk 2.3 with one with the spherical surface loading blocks 2.2 cooperation, the hydraulic cylinder array 2.1 of each point pass through
Load is applied to the spherical surface plummer 2.4 on loading disc 2.3 by spherical surface loading blocks 2.2；
By computer control system control hydraulic loaded circuit (including one by the first of electro-hydraulic proportion reversing valve control
Hydraulic circuit and N-1 the second hydraulic circuits controlled respectively by regular tap reversal valve) electro-hydraulic proportion reversing valve aperture
With the load access number of N-1 regular tap reversal valve, to control the axially loaded cylinder in left end, the axially loaded cylinder of right end, radial direction
The loading force of cylinder is loaded, while loading force passes to loading disc 2.3, and then loading force is transmitted on main shaft 2.7 by bearing,
Blower five degree of freedom load F is completed by the combination of each loading forcex, Fy, Fz, My, MzLoad.
Fig. 1 is the coordinate diagram of the blower six degree of freedom load of invention.Wherein coordinate system is defined as follows: X-axis is along main shaft square
To direction downbeam, Z axis is 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.FxIndicate the loading force of X-axis positive direction, FyIndicate the loading force of Y-axis positive direction, FzIndicate the loading force of Z axis positive direction, My
Indicate overturning moment, MzIndicate yaw moment of flexure, above-mentioned composition five degree of freedom load of the invention, in addition, MxIndicate driving mechanism band
The torque that dynamic main shaft 2.7 rotates.
Fig. 2 is driving mechanism, the overall connection structure diagram of five degree of freedom load charger, blower.It is load by test specimen 1
Power effective object, is fixed on the ground by pedestal.Five degree of freedom load charger 2 passes through the axially loaded cylinder group in left end, a left side
It holds axially loaded cylinder group, radial loaded cylinder group to apply load to loading disc, and then load is applied to by test specimen 1 by main shaft, respectively
Loading force combination is completed to by five freedom degree load F of test specimenx, Fy, Fz, My, MzLoad；Driving mechanism 4 is right by shaft coupling 3
M is applied by test specimen 1xLoad is rotated with driving spindle.
Fig. 3 is the structure chart of five degree of freedom load charger.The outer housing includes the left housing for being bolted connection
Body 2.6 and right shell body 2.8, the affixed support frame 2.5 in the lower end of the outer housing, the load cylinder 5.1 being fixedly connected on outer housing
Load is applied to loading disc 2.3, and then 2.9 main shaft 2.7 of bearing by connecting between loading disc 2.3 and main shaft 2.7 applies load
Lotus.Outer housing is used to support to fix the load cylinder 5.1 of each point.
In the present embodiment, the bearing 2.9 connected between the loading disc 2.3 and main shaft 2.7 is that can bear axial push away
The thrust bearing of power.
Fig. 5 is the loading structure figure of the hydraulic cylinder array of each point of loading disc.Five degree of freedom load charger also wraps
The fixed frame 2.12 affixed by screw 2.11 with the outer housing is included, is equipped in fixed frame 2.12 N number of sliding for leading power block 2.13
Capable sliding slot, lead power block 2.13 rear end open up accommodate spring 2.10 groove, the front end of spring 2.10 with lead 2.13 phase of power block
It supports, the rear end of spring 2.10 and the piston rod of load cylinder offset, the position of N number of sliding slot and N number of load cylinder 5.1 in fixed frame 2.12
Corresponding, the front end of each power of leading block 2.13 connects a spherical surface loading blocks 2.2, each power of leading block 2.13 and spherical surface loading blocks jointly
2.2 connect to contradict；
Then, the piston rod of each load cylinder 5.1, which passes through spring 2.9 and leads power block 2.13, is transmitted to spherical surface for loading force
Loading blocks 2.2 always add the output of hydraulic cylinder array 2.1 finally by spherical surface loading blocks 2.2 and the cooperation of spherical surface plummer 2.4
Power is carried to be applied on loading disc 2.3.Spring 2.10 plays the role of buffering and preloading, and spherical surface loading blocks 2.2 and spherical surface carry
The cooperation of platform 2.4 is so that the load of hydraulic cylinder array 2.1 is more concentrated, and overcomes the different load cylinder loads of hydraulic cylinder array 2.1
When hydraulic cylinder array 2.1 point of resultant force to main-shaft axis distance difference.
Fig. 6 is the structure chart in the hydraulic loaded circuit of each point of loading disc of the embodiment of the present invention.The figure is with each point
The hydraulic cylinder array of position includes that 4 load cylinders are illustrated, and a load cylinder 5.1a is changed by electric-hydraulic proportion in this four load cylinders
It is controlled to valve, oil circuit is the first hydraulic circuit, and the other three load cylinder is controlled by regular tap reversal valve respectively, and oil circuit is
Second hydraulic circuit；
First hydraulic circuit includes fuel tank 5.10, pump 5.11, high pressure filter 5.8, check valve 5.7, electric-hydraulic proportion
Reversal valve 5.5, hydraulic lock 5.3a, load cylinder 5.1a, return filter 5.16, thermoregulator 5.15, the high pressure filter
5.8 outlet is connected with overflow valve 5.9, and it is poor that the inlet and outlet of the electro-hydraulic proportion reversing valve 5.5 is connected with limited pressure level pressure
Import pressure-reducing pressure compensator 5.4, effect is to keep the pressure difference of inlet and outlet constant, so that electro-hydraulic proportion reversing valve 5.5
Flow determine that the entrance of the electro-hydraulic proportion reversing valve 5.5 is also connected with pressure switch 5.6, described electro-hydraulic by its aperture
Proportional reversing valve 5.5 is three position four-way directional control valve, and the left position of the three position four-way directional control valve corresponds to the load of load cylinder, and interposition is
Disconnect, the oil inlet pipe of the off-load of the corresponding load cylinder in right position, the load cylinder 5.1a connects temperature and pressure transmitter 5.2；
Second hydraulic circuit includes fuel tank 5.10, 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), load cylinder (5.1b, 5.1c, 5.1d), oil return
Filter 5.16, thermoregulator 5.15, the regular tap reversal valve (5.17a, 5.17b, 5.17c) are 3-position 4-way commutation
Valve, the load of the corresponding load cylinder in the left position of the three position four-way directional control valve, interposition is to disconnect, and the corresponding load cylinder in right position unloads
Lotus.Fuel tank 5.10, pump 5.11, high pressure filter 5.8, check valve 5.7, oil return in first hydraulic circuit and the second hydraulic circuit
Filter 5.16, thermoregulator 5.15 constitute the common main line of the two.
The hydraulic lock (5.3a, 5.3b, 5.3c, 5.3d) is made of two hydraulic control one-way valves that hydraulic control each other connects, when
When one of hydraulic control one-way valve oil inlet, the control oil circuit of another hydraulic control one-way valve, which obtains oil liquid, return valve port opening can
Oil.
When load, computer control system obtains the load of the hydraulic cylinder array of each point by load decomposition computation
Power controls the power output of each load cylinder of hydraulic cylinder array according to the size of loading force.Start motor 5.14, passes through shaft coupling
5.13 drive pump 5.11, and hydraulic oil is single by high pressure filter 5.8 after 5.11 pressurization of pump via oil absorption filter 5.12
To valve 5.7, main line feed system working solution pressure oil is formed.
Defining each load cylinder maximum output loading force is Fa, by the loading force of the load cylinder of electro-hydraulic proportion reversing valve control
For F0, the loading force of the load cylinder each controlled by regular tap reversal valve is Fi(i=1,2,3), then F0∈ [0, Fa], Fi∈
{ 0, Fa, the then total loading force of output of the hydraulic cylinder array of each point
When computer control system calculates 0 < F≤F of loading force of resulting hydraulic cylinder arrayaWhen, it is commutated by electric-hydraulic proportion
The control load of valve 5.5 cylinder 5.1a is individually loaded, while loading cylinder 5.1b, load cylinder 5.1c and load cylinder 5.1d off-load.The operating condition
Under, in-line are as follows: oil absorption filter 5.12, pump 5.11, high pressure filter 5.8, check valve 5.7, electro-hydraulic proportion reversing valve 5.5 are left
Position, the left position hydraulic lock 5.3a load cylinder 5.1a rodless cavity.Oil return line are as follows: load cylinder 5.1a rod chamber, the right position hydraulic lock 5.3a,
5.5 left position of electro-hydraulic proportion reversing valve, return filter 5.16, thermoregulator 5.15, fuel tank 5.10.
As the loading force F for calculating resulting hydraulic cylinder arraya< F≤2FaWhen, added by what electro-hydraulic proportion reversing valve 5.5 controlled
The load cylinder 5.1b for carrying cylinder 5.1a, regular tap reversal valve 5.17a control is loaded jointly, while loading cylinder 5.1c and load cylinder
5.1d off-load.Under the operating condition, in-line are as follows: oil absorption filter 5.12, pump 5.11, high pressure filter 5.8, check valve 5.7, then pass through
By the oil inlet passage of each branch；Wherein load the oil inlet passage of cylinder 5.1a branch are as follows: 5.5 left position of electro-hydraulic proportion reversing valve, liquid
The pressure lock left position 5.3a, loads cylinder 5.1a rodless cavity；Wherein load the oil inlet passage of cylinder 5.1b branch are as follows: regular tap reversal valve
The left position 5.17a, the left position hydraulic lock 5.3b load cylinder 5.1b rodless cavity.Oil return line are as follows: converged via the drainback passage of each branch
Always, using return filter 5.16, thermoregulator 5.15 returns to fuel tank 5.10；Wherein load the oil return of cylinder 5.1a branch
Channel are as follows: load cylinder 5.1a rod chamber, the right position hydraulic lock 5.3a, 5.5 left position of electro-hydraulic proportion reversing valve；Wherein load cylinder 5.1b branch
The drainback passage on road are as follows: load cylinder 5.1b rod chamber, the right position hydraulic lock 5.3b, the left position regular tap reversal valve 5.17a.
As the loading force 2F for calculating resulting hydraulic cylinder arraya< F≤3FaWhen, it is controlled by electro-hydraulic proportion reversing valve 5.5
Load load cylinder 5.1b and regular tap reversal valve the 5.17b control of cylinder 5.1a, regular tap reversal valve 5.17a control
Load cylinder 5.1c is loaded jointly, while loading cylinder 5.1d off-load.Under the operating condition, in-line are as follows: oil absorption filter 5.12, pump
5.11, high pressure filter 5.8, check valve 5.7, then the oil inlet passage via each branch；Wherein load cylinder 5.1a branch into
Oily channel are as follows: 5.5 left position of electro-hydraulic proportion reversing valve, the left position hydraulic lock 5.3a load cylinder 5.1a rodless cavity；Wherein load cylinder 5.1b
The oil inlet passage of branch are as follows: the left position regular tap reversal valve 5.17a, the left position hydraulic lock 5.3b load cylinder 5.1b rodless cavity；Wherein
Load the oil inlet passage of cylinder 5.1c branch are as follows: the left position regular tap reversal valve 5.17b, the left position hydraulic lock 5.3c load cylinder 5.1c
Rodless cavity.Oil return line are as follows: the drainback passage via each branch summarizes, using return filter 5.16, thermoregulator
5.15, return to fuel tank 5.10；Wherein load the drainback passage of cylinder 5.1a branch are as follows: load cylinder 5.1a rod chamber, hydraulic lock 5.3a
Right position, 5.5 left position of electro-hydraulic proportion reversing valve；Wherein load the drainback passage of cylinder 5.1b branch are as follows: load cylinder 5.1b rod chamber, liquid
The pressure lock right position 5.3b, the left position regular tap reversal valve 5.17a；Wherein load the drainback passage of cylinder 5.1c branch are as follows: load cylinder
5.1c rod chamber, the right position hydraulic lock 5.3c, the left position regular tap reversal valve 5.17b.
As the loading force 3F for calculating resulting hydraulic cylinder arraya< F≤4FaWhen, it is controlled by electro-hydraulic proportion reversing valve 5.5
Load the load cylinder 5.1b of cylinder 5.1a, regular tap reversal valve 5.17a control, the load of regular tap reversal valve 5.17b control
The load cylinder 5.1d of cylinder 5.1c and regular tap reversal valve 5.17c control is loaded jointly.Under the operating condition, in-line are as follows: oil suction
Filter 5.12, pump 5.11, high pressure filter 5.8, check valve 5.7, then the oil inlet passage via each branch；Wherein load cylinder
The oil inlet passage of 5.1a branch are as follows: 5.5 left position of electro-hydraulic proportion reversing valve, the left position hydraulic lock 5.3a load cylinder 5.1a rodless cavity；Its
The oil inlet passage of middle load cylinder 5.1b branch are as follows: the left position regular tap reversal valve 5.17a, the left position hydraulic lock 5.3b load cylinder
5.1b rodless cavity；Wherein load the oil inlet passage of cylinder 5.1c branch are as follows: the left position regular tap reversal valve 5.17b, hydraulic lock 5.3c
Left position loads cylinder 5.1c rodless cavity；Wherein load the oil inlet passage of cylinder 5.1d branch are as follows: the left position regular tap reversal valve 5.17c,
The left position hydraulic lock 5.3d loads cylinder 5.1d rodless cavity.Oil return line are as follows: the drainback passage via each branch summarizes, using return
Oil strainer 5.16, thermoregulator 5.15 return to fuel tank 5.10；Wherein load the drainback passage of cylinder 5.1a branch are as follows: load
Cylinder 5.1a rod chamber, the right position hydraulic lock 5.3a, 5.5 left position of electro-hydraulic proportion reversing valve；The oil return for wherein loading cylinder 5.1b branch is logical
Road are as follows: load cylinder 5.1b rod chamber, the right position hydraulic lock 5.3b, the left position regular tap reversal valve 5.17a；Wherein load cylinder 5.1c branch
The drainback passage on road are as follows: load cylinder 5.1c rod chamber, the right position hydraulic lock 5.3c, the left position regular tap reversal valve 5.17b；Wherein plus
Carry the drainback passage of cylinder 5.1d branch are as follows: load cylinder 5.1d rod chamber, the right position hydraulic lock 5.3d, regular tap reversal valve 5.17c
Left position.
When off-load, electro-hydraulic proportion reversing valve 5.5 and the right position work of regular tap reversal valve (5.17a, 5.17b, 5.17c).
Under the operating condition, in-line are as follows: oil absorption filter 5.12, pump 5.11, high pressure filter 5.8, check valve 5.7, then via each
The oil inlet passage on road；Wherein load the oil inlet passage of cylinder 5.1a branch are as follows: the right position of electro-hydraulic proportion reversing valve 5.5, hydraulic lock 5.3a
Right position loads cylinder 5.1a rod chamber；Wherein load the oil inlet passage of cylinder 5.1b branch are as follows: the right position regular tap reversal valve 5.17a,
The right position hydraulic lock 5.3b loads cylinder 5.1b rod chamber；Wherein load the oil inlet passage of cylinder 5.1c branch are as follows: regular tap reversal valve
The right position 5.17b, the right position hydraulic lock 5.3c load cylinder 5.1c rod chamber；Wherein load the oil inlet passage of cylinder 5.1d branch are as follows: common
The right position reversal valve 5.17c is switched, the right position hydraulic lock 5.3d loads cylinder 5.1d rod chamber.Oil return line are as follows: via returning for each branch
Oily channel is summarized, and using return filter 5.16, thermoregulator 5.15 returns to fuel tank 5.10；Wherein load cylinder 5.1a branch
The drainback passage on road are as follows: load cylinder 5.1a rodless cavity, the left position hydraulic lock 5.3a, the right position of electro-hydraulic proportion reversing valve 5.5；Wherein load
The drainback passage of cylinder 5.1b branch are as follows: load cylinder 5.1b rodless cavity, the left position hydraulic lock 5.3b, regular tap reversal valve 5.17a are right
Position；Wherein load the drainback passage of cylinder 5.1c branch are as follows: load cylinder 5.1c rodless cavity, the left position hydraulic lock 5.3c, regular tap change
To the right position valve 5.17b；Wherein load the drainback passage of cylinder 5.1d branch are as follows: load cylinder 5.1d rodless cavity, the left position hydraulic lock 5.3d,
The right position regular tap reversal valve 5.17c.
When electro-hydraulic proportion reversing valve 5.5, regular tap reversal valve (5.17a, 5.17b, 5.17c) power loss, the two is in
Interposition is in off state, and hydraulic lock is in the lock state, then each branch by corresponding hydraulic lock (5.3a, 5.3b, 5.3c,
5.3d) pressure maintaining.
In loading procedure, the loading force of load cylinder 5.1 is detected by temperature and pressure transmitter 5.2, and feeds back to computer
Control system realizes loading force program and the synchronized Coordinative Control by industrial personal computer and software programming.5.6 detection system of pressure switch
System oil pressure, when oil pressure is excessively high, pressure switch 5.6 is acted, and acoustooptic alarm system alarm reminds staff to overhaul.
As the load cylinder quantity N > 4 or 2N3 of hydraulic cylinder array, working principle is as above.Wherein have 1 load cylinder by
Electro-hydraulic proportion reversing valve control, remaining N-1 load cylinder are controlled by regular tap reversal valve, the hydraulic cylinder array of each point
Exporting total loading force isAperture and the N-1 for controlling electro-hydraulic proportion reversing valve according to the actual situation are a general
The load access number for closing reversal valve is opened up, [0, N × F can be obtaineda] any loading force in range.
The above is merely preferred embodiments of the present invention, be not intended to limit the invention, it is all in spirit of the invention and
Made any modifications, equivalent replacements, and improvements etc., should all be included in the protection scope of the present invention within principle.
Claims (5)
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| CN110005646B (en) * | 2019-04-01 | 2020-03-03 | 浙江大学 | A digital electro-hydraulic loading device suitable for large load range and its loading method |
| CN115508091B (en) * | 2022-11-07 | 2023-03-10 | 烟台天成机械有限公司 | Wind generating set main shaft, driftage, change oar bearing capability test platform |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1564405A1 (en) * | 2004-02-10 | 2005-08-17 | Gamesa Eolica, S.A. (Sociedad Unipersonal) | Test bench for wind turbines |
| CN102156047A (en) * | 2011-04-02 | 2011-08-17 | 浙江大学 | Loading simulation device for test bed of wind turbine |
| CN102636367A (en) * | 2012-04-23 | 2012-08-15 | 浙江大学 | Multi-degree-of-freedom dynamic loading device for simulating wind power and ocean current load |
| CN103900818A (en) * | 2014-03-10 | 2014-07-02 | 浙江大学 | Static pressure oil cavity loading system and method for recurrence of wind turbine five-degree-of-freedom load |
| CN104792564A (en) * | 2015-04-30 | 2015-07-22 | 国电联合动力技术有限公司 | Loading system applied to wind turbine unit testbed and application of loading system |
| CN106017920A (en) * | 2016-06-24 | 2016-10-12 | 湖南科技大学 | Wind load generator set driving chain mechanics characteristic simulation system and simulation method thereof |
-
2016
- 2016-12-27 CN CN201611226874.4A patent/CN106813935B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1564405A1 (en) * | 2004-02-10 | 2005-08-17 | Gamesa Eolica, S.A. (Sociedad Unipersonal) | Test bench for wind turbines |
| CN102156047A (en) * | 2011-04-02 | 2011-08-17 | 浙江大学 | Loading simulation device for test bed of wind turbine |
| CN102636367A (en) * | 2012-04-23 | 2012-08-15 | 浙江大学 | Multi-degree-of-freedom dynamic loading device for simulating wind power and ocean current load |
| CN103900818A (en) * | 2014-03-10 | 2014-07-02 | 浙江大学 | Static pressure oil cavity loading system and method for recurrence of wind turbine five-degree-of-freedom load |
| CN104792564A (en) * | 2015-04-30 | 2015-07-22 | 国电联合动力技术有限公司 | Loading system applied to wind turbine unit testbed and application of loading system |
| CN106017920A (en) * | 2016-06-24 | 2016-10-12 | 湖南科技大学 | Wind load generator set driving chain mechanics characteristic simulation system and simulation method thereof |
Non-Patent Citations (2)
| Title |
|---|
| 复现风力机五自由度载荷的加载控制方法;殷秀兴 等;《浙江大学学报(工学版)》;20150815;第49卷(第8期);第1470-1477、1502页 |
| 大型风电机组测试平台加载装置的优化设计;童星 等;《可再生能源》;20151020;第33卷(第10期);第1508-1511页 |
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