CN207083526U - Combined harvester backhaul plate and vibratory sieve inertial force balancing device - Google Patents
Combined harvester backhaul plate and vibratory sieve inertial force balancing device Download PDFInfo
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- CN207083526U CN207083526U CN201720404360.7U CN201720404360U CN207083526U CN 207083526 U CN207083526 U CN 207083526U CN 201720404360 U CN201720404360 U CN 201720404360U CN 207083526 U CN207083526 U CN 207083526U
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- vibratory sieve
- backhaul plate
- backhaul
- sieve
- plate
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Abstract
It the utility model is related to combined harvester vibratory sieve and backhaul plate inertial force balancing device, including backhaul plate and vibratory sieve, backhaul plate includes backhaul plate face, one end of backhaul plate face is provided with backhaul plate roller, other end is provided with backhaul plate bias axis of rocking, and the both ends of backhaul plate bias axis of rocking are provided with backhaul plate balance weight assembly；Vibratory sieve includes sieve nest, and one end of sieve nest is provided with vibratory sieve roller, and other end is provided with vibratory sieve bias axis of rocking, and vibratory sieve is connected with backhaul plate by chain, and the wrapping of the vibratory sieve and the chain on the backhaul plate is in opposite direction.The utility model draws inertia force in the horizontal counteracting ratio η with vertical direction by theory analysis1And η2, and then overall required optimal counterweight is drawn, and the adjustable counter weight device of quality is devised, weight stack quantity can be changed according to actual conditions counterweight is adjusted to optimal parameter.
Description
Technical field
It the utility model is related to a kind of combined harvester vibratory sieve and backhaul plate inertial force balancing device and balance method.
Background technology
Vibratory sieve and backhaul plate are that the important of combined harvester cleans workpiece, due to inertia caused by reciprocating motion
Power, there is the problems such as big to frame impact, noise is big；Especially as China's combined harvester increasingly to maximization direction hair
Exhibition, the harmful effect for eliminating inertia force also increasingly draw attention.Traditional balance of shaking force counterweight uses Experience Design side more
Method, it is not accurate enough, and the reciprocating motion that often have ignored backhaul plate and vibratory sieve can play negative function to inertia force, not from
The two overall balance for considering inertia force.
Chinese patent CN204458789U discloses a kind of angled type reciprocating-piston compressor of balance of shaking force optimization, should
Patent proposes a kind of balance of shaking force New Optimizing Method, the rotating inertia force of compressor and reciprocal inertia force is all obtained preferably
Balance；Counterweight is arranged on base bearing side by the patent, and such a installation site is limited larger by space.Patent CN104847859A
A kind of range-adjustable and the slider-crank mechanism of autobalance inertia force proposed；The crank that the utility model is expanded by crank
Slide block structure collocation spline fitted, realizes the variable reciprocating stroke a little of sliding block, utilizes the geometry and matter of splined builtup
Measure the rational design of distribution so that mechanism can realize the partial equilibrium of inertia force in arbitrarily regulation reciprocating stroke；The patent
It is relatively small suitable for the machine driving of small reciprocating stroke, operation strategies.
Rotated counterclockwise for backhaul plate drive shaft, in the two motion process caused by vibratory sieve drive shaft rotates clockwise
Inertia force offset effect, by the inertia force of vibratory sieve and backhaul plate by move horizontally inertia force and rotating inertia force respectively by
Horizontally and vertically decompose, the inertia force in horizontally and vertically both directions can all be offset, and its total inertia force can also reduce.
Utility model content
For combined harvester during harvest, junction is easy caused by inertia force caused by backhaul plate and vibratory sieve
Destroy, noise utilizes backhaul plate and vibration with the problems such as larger, the utility model is vibrated from inertia force population equilibrium angle
Inertia force caused by sieving mutual movement relation offsets situation, analyzes the degree of inertia force reduction in theory, it is proposed that a kind of
For the method for inertia force population equilibrium method and counterbalance design with move toward one another mechanism.
The utility model is to realize above-mentioned technical purpose by following technological means：Combined harvester backhaul plate and vibration
Inertial force balancing device is sieved, including backhaul plate and vibratory sieve, the backhaul plate include backhaul plate face, one end of the backhaul plate face
Backhaul plate roller is installed, other end is provided with backhaul plate bias axis of rocking, the both ends peace of the backhaul plate bias axis of rocking
Equipped with backhaul plate balance weight assembly；The vibratory sieve includes sieve nest, and one end of the sieve nest is provided with vibratory sieve roller, other end
Vibratory sieve bias axis of rocking is installed, the vibratory sieve is connected with the backhaul plate by chain, the vibratory sieve with described time
The wrapping of chain on journey plate is in opposite direction.
In such scheme, the backhaul plate balance weight assembly includes backhaul plate sprocket wheel and backhaul plate weight stack, the backhaul plate
Sprocket wheel is located at the both ends of the backhaul plate bias axis of rocking, and is all provided with the backhaul plate sprocket wheel and the backhaul plate weight stack
One mounting hole, the backhaul plate weight stack are bolted to connection on the backhaul plate sprocket wheel.
In such scheme, the vibratory sieve balance weight assembly includes vibratory sieve sprocket wheel and vibratory sieve weight stack, the vibratory sieve
Sprocket wheel is located at the both ends of the vibratory sieve bias axis of rocking, and is all provided with the vibratory sieve sprocket wheel and the vibratory sieve weight stack
Two mounting holes, the vibratory sieve weight stack are bolted to connection on the vibratory sieve sprocket wheel.
In such scheme, the backhaul plate weight stack material is cast iron.
In such scheme, the material of the vibratory sieve weight stack is cast iron.
It is provided by the utility model to realize inertia force with vibratory sieve inertial force balancing device using combined harvester backhaul plate
The method of balance, comprises the following steps：
S1：Backhaul plate and vibratory sieve are reduced to slider-crank mechanism, wherein backhaul plate roller is reduced to sliding block, backhaul
Plate face is reduced to connecting rod, backhaul plate bias axis of rocking is reduced to crank, backhaul plate balance weight assembly is reduced to balancing weight；Vibratory sieve rolls
Wheel is reduced to sliding block, sieve nest is reduced to connecting rod, vibratory sieve bias axis of rocking is reduced to crank, vibratory sieve balance weight assembly is reduced to match somebody with somebody
Pouring weight；
By the slider-crank mechanism inertia force dynamic analysis of classics：Slider-crank mechanism inertia force has：Lumped mass at B
mBLocate rotation inertia force FBWith lumped mass m at CcThe mobile inertia force F in placeC
R is crank length in formula,For crank rotation angle speed, θ is the corner of crank；
For above-mentioned inertia force by adding certain counterweight to carry out the part of inertia force to the reverse suitable distance of backhaul plate crank
Balance；Turn round inertia force FBCan be by adding quality m at swivel point r' DD1It is balanced：
I.e.：mD1=r/r'mB
It is same for mCCaused mobile inertia force in the horizontal direction, it is further added by a balance mass mD2Carry out inertia force
Balance；As known from the above, for total counterweight m of slider-crank mechanism balance of shaking forceDM is formed by two partsD1And mD2；I.e.：
mD=mD1+kmD2=r/r ' (mB+kmC)
Note：By counterweight mD2Before quality plus certain coefficient k, be allowed to can balance slide block horizontal direction inertia force, it is and unlikely
In making, vertical direction inertia force is excessive, and general k takes 1/3-1/2；
S2：The each several part mass concentration of crank block is replaced B, C at and then with adding balance mass block to enter in step S1
Row balance of shaking force；Likewise, when carrying out population equilibrium consideration, backhaul plate and vibratory sieve quality are each concentrated into replacement and B,
C and B ', C ' place, then respective lumped mass block mCAnd mC′At C with the caused inertia force of C '：
Wherein：cosθ1=cos (- ω t+ α)
cosθ2=cos (ω t+ β)
α and β is backhaul plate crank initial angle and vibratory sieve initial angle；ω is crank rotation angle speed；Rotated with vibratory sieve
Angular speed is just FCFor the horizontal inertial force of backhaul plate, FC′For vibratory sieve horizontal inertial force；
Known by formula above：It is oppositely oriented when driving, in motion process, have the feelings that inertia force is offset by motion
Condition, following discussion inertia force cancellation level, and then for choose more suitably balance mass do theory analysis；By backhaul plate with
Vibratory sieve horizontal inertial force is added, then total inertia force of any time horizontal direction is FCC′：
The average inertia power size of a cycle is carried out during by the average inertia power size of a cycle with not considering to offset
Compare；
Wherein：T is the swing circle of vibratory sieve or backhaul plate, η1Proportionality coefficient；
Likewise, also inertia force counteracting can be carried out with similar method in the inertia force to rotating part；For backhaul plate
mBWith vibratory sieve mB′Caused revolution inertia force is respectively decomposed inertia force by X-direction and Y-direction：
Horizontal direction：
Vertical direction：
Then any time make a concerted effort：
Then the inertia force average within any one cycle after population equilibrium and the inertia force average for not considering to offset are carried out
Compare η2；
S3：Overall balance of shaking force, can reduce overall inertia force, and corresponding major part counterweight also reduces；In backhaul
During plate combines with vibratory sieve, vibratory sieve quality is larger, and backhaul plate plays a part of offsetting to be sieved with balance vibration；The specific matter reduced
Amount and proportionality coefficient η1And η2It is relevant, therefore the optimal weight mass m of vibratory sieveD′；
Then corresponding vibratory sieve horizontal equilibrium quality：
Then corresponding vibratory sieve spin balancing quality：
So the optimal weight mass of vibratory sieve is：
The beneficial effects of the utility model are：(1) the utility model is in traditional crank slide block mechanism inertia force power credit
On the basis of analysis, power analysis is carried out with vertical direction power with regard to horizontal respectively to the backhaul plate with out movement and vibratory sieve, obtained
Go out the degree that total inertia force reduces, chosen for the counterweight of backhaul plate and vibratory sieve and support is provided；Set before theoretically solving
Meter two parts inertia force is individually calculated, the individually designed weak point of counterweight, at the same such a theoretical method draw match somebody with somebody heavy
Amount is lighter, and overall balance of shaking force is more preferable, reaches and reduces the possibility that machine destroys by inertia force, the purpose of vibration and noise reducing.(2)
The counterweight adjustable component of design, i.e., be provided with mounting hole on sprocket wheel and weighting distribution wheel, for installing sheet weight stack, solves and sets in the past
Counterweight is that a monoblock cast iron is not easy to exchange the problems such as installation is inconvenient in meter, and counterweight adjustable component can be simple fast according to actual conditions
Changeing for speed, makes balance of shaking force optimal.
Brief description of the drawings
Fig. 1 is backhaul plate of the present utility model and vibratory sieve front view.
Fig. 2 is backhaul plate overview of the present utility model.
Fig. 3 is vibratory sieve overview of the present utility model.
Fig. 4 is backhaul plate balance weight assembly overview of the present utility model.
Fig. 5 is vibratory sieve balance weight assembly partial view of the present utility model.
Fig. 6 is backhaul plate of the present utility model and Structure of Vibrating Screen sketch.
Fig. 7 is slider-crank mechanism kinetic model figure of the present utility model.
Fig. 8 is revolution inertia force decomposing schematic representation of the present utility model.
In figure, 1- backhauls plate, 2- vibratory sieves, 3- chains；101- backhaul plates roller, 102- backhauls plate face, 103- backhaul plates
Eccentric axis of rocking, 104- backhaul plates balance weight assembly, 201- vibratory sieves roller, 202- sieve nests, 201- vibratory sieve bias axis of rocking,
204-1 vibratory sieve balance weight assemblies；104-1- backhaul plates sprocket wheel, 104-2- backhaul plates weight stack, 104-3- mounting holes；204-1- shakes
Dynamic sieve sprocket wheel, 204-2- vibratory sieves weight stack, 204-3- counterweight mounting holes.
Embodiment
Below in conjunction with the accompanying drawings and specific embodiment is further described to the utility model, but guarantor of the present utility model
Shield scope is not limited to this.
Backhaul plate described in the utility model and vibratory sieve totality inertial force balancing device, its structure as shown in Figure 1, Figure 2, Fig. 3
It is shown, including：Backhaul plate roller 101, backhaul plate face 102, backhaul plate bias axis of rocking 103, backhaul plate balance weight assembly 104；Shake
Dynamic sieve 2 include vibratory sieve roller 201, sieve nest 202, vibratory sieve bias axis of rocking 203, the vibratory sieve 2 of vibratory sieve balance weight assembly 204 with
Backhaul plate 1 is connected by chain 3, enters action edge transmission, and vibratory sieve 2 and backhaul plate 1 are by the reserved packet of chain 3 around therefore the two drives
In the opposite direction.
As shown in figure 4, the backhaul plate balance weight assembly 104 includes backhaul plate sprocket wheel 104-1, backhaul plate weight stack 104-2,
Backhaul plate weight stack 104-2 materials are cast iron；Mounting hole is all provided with backhaul plate sprocket wheel 104-1 and backhaul plate weight stack 104-2
104-3, by bolt a number of backhaul plate weight stack 104-2 be arranged on and backhaul plate sprocket wheel 104 lateral surface on；
As shown in figure 5, the vibratory sieve balance weight assembly 204 includes vibratory sieve sprocket wheel 204-1, vibratory sieve weight stack 204-2,
Vibratory sieve weight stack 204-2 materials are cast iron；Counterweight peace is all provided with vibratory sieve sprocket wheel 204-1 and vibratory sieve weight stack 204-2
Fill hole 204-3, by bolt a number of vibratory sieve weight stack 204-2 be arranged on and vibratory sieve sprocket wheel 204 outside
On face.
As shown in fig. 6, backhaul plate 1 and vibratory sieve 2 can be reduced to slider-crank mechanism, wherein backhaul plate roller 101
It is reduced to sliding block, backhaul plate face 102 is reduced to connecting rod, backhaul plate bias axis of rocking 103 is reduced to crank, backhaul plate balance weight assembly
104 are reduced to balancing weight；Vibratory sieve roller 201 is reduced to sliding block, sieve nest 202 is reduced to connecting rod, vibratory sieve bias axis of rocking 203
It is reduced to crank, the balancing weight of vibratory sieve balance weight assembly 204；
S1：By the slider-crank mechanism inertia force dynamic analysis of classics：Slider-crank mechanism inertia force has：Concentrated at B
Quality mBLocate rotation inertia force FBWith lumped mass m at CcThe mobile inertia force F in placeC
R is crank length in formula,For crank rotation angle speed, θ is the corner of crank.
For above-mentioned inertia force typically by adding certain counterweight to carry out inertia force to the reverse suitable distance of backhaul plate crank
Partial equilibrium；Turn round inertia force FBCan be by adding quality m at swivel point r' DD1It is balanced：
I.e.：mD1=r/r'mB
It is same for mCCaused mobile inertia force in the horizontal direction, a balance mass m can be further added byD2Carry out inertia
Dynamic balance.As known from the above, for total counterweight m of slider-crank mechanism balance of shaking forceDM is formed by two partsD1And mD2；I.e.：
mD=mD1+kmD2=r/r ' (mB+kmC)
Note：By counterweight mD2Before quality plus certain coefficient k, be allowed to can balance slide block horizontal direction inertia force, it is and unlikely
In making, vertical direction inertia force is excessive, and general k takes 1/3-1/2.
S2：The each several part mass concentration of crank block is replaced B, C at and then with adding balance mass block to enter in step S1
Row balance of shaking force；Likewise, when carrying out population equilibrium consideration, backhaul plate and vibratory sieve quality are each concentrated into replacement and B,
C and B ', C ' place, then respective lumped mass block mCAnd mC′At C with the caused inertia force of C '：
Wherein：cosθ1=cos (- ω t+ α)
cosθ2=cos (ω t+ β)
α and β is backhaul plate crank initial angle and vibratory sieve initial angle；ω is crank rotation angle speed；Rotated with vibratory sieve
Angular speed is just FCFor the horizontal inertial force of backhaul plate, FC′For vibratory sieve horizontal inertial force.
Known by formula above：It is oppositely oriented when driving, in motion process, have the feelings that inertia force is offset by motion
Condition, following discussion inertia force cancellation level, and then for choose more suitably balance mass do theory analysis；By backhaul plate with
Vibratory sieve horizontal inertial force is added, then total inertia force of any time horizontal direction is FCC′：
The average inertia power size of a cycle is carried out during by the average inertia power size of a cycle with not considering to offset
Compare；
Wherein：T is the swing circle of vibratory sieve or backhaul plate, η1Proportionality coefficient.
Likewise, also inertia force counteracting can be carried out with similar method in the inertia force to rotating part；For backhaul plate
mBWith vibratory sieve mB′Caused revolution inertia force is respectively decomposed inertia force by X-direction and Y-direction：
Horizontal direction：
Vertical direction：
Then any time make a concerted effort：
Then the inertia force average within any one cycle after population equilibrium and the inertia force average for not considering to offset are carried out
Compare η2；
S2：Overall balance of shaking force, can reduce overall inertia force, and corresponding major part counterweight also reduces；In backhaul
During plate combines with vibratory sieve, vibratory sieve quality is larger, and backhaul plate plays a part of offsetting to be sieved with balance vibration；The specific matter reduced
Amount and proportionality coefficient η1And η2It is relevant, therefore the optimal weight mass m of vibratory sieveD′；
Then corresponding vibratory sieve horizontal equilibrium quality：
Then corresponding vibratory sieve spin balancing quality：
So the optimal weight mass of vibratory sieve is：
It using the above method, can not only make the more preferable of overall balance of shaking force, and can reduce and overall match somebody with somebody heavy
Amount, reduces unnecessary energy consumption.
Claims (5)
1. combined harvester backhaul plate and vibratory sieve inertial force balancing device, including backhaul plate（1）And vibratory sieve（2）, its feature
It is, the backhaul plate（1）Including backhaul plate face（102）, the backhaul plate face（102）One end backhaul plate roller is installed
（101）, other end is provided with backhaul plate bias axis of rocking（103）, the backhaul plate bias axis of rocking（103）Both ends installation
There is backhaul plate balance weight assembly（104）；The vibratory sieve（2）Including sieve nest（202）, the sieve nest（202）One end be provided with and shake
Dynamic sieve roller（201）, other end is provided with vibratory sieve bias axis of rocking（203）, the vibratory sieve（2）With the backhaul plate
（1）Pass through chain（3）Connection, the vibratory sieve（2）With the backhaul plate（1）On chain（3）Wrapping it is in opposite direction.
2. combined harvester backhaul plate according to claim 1 and vibratory sieve inertial force balancing device, it is characterised in that institute
State backhaul plate balance weight assembly（104）Including backhaul plate sprocket wheel（104-1）With backhaul plate weight stack（104-2）, the backhaul plate chain
Wheel（104-1）Positioned at the backhaul plate bias axis of rocking（103）Both ends, the backhaul plate sprocket wheel（104-1）With the backhaul
Plate weight stack（104-2）On be all provided with the first mounting hole（104-3）, the backhaul plate weight stack（104-2）It is bolted
It is connected to the backhaul plate sprocket wheel（104-1）On.
3. combined harvester backhaul plate according to claim 2 and vibratory sieve inertial force balancing device, it is characterised in that institute
State vibratory sieve balance weight assembly（204）Including vibratory sieve sprocket wheel（204-1）With vibratory sieve weight stack（204-2）, the vibratory sieve chain
Wheel（204-1）Positioned at the vibratory sieve bias axis of rocking（203）Both ends, the vibratory sieve sprocket wheel（204-1）With the vibration
Sieve weight stack（204-2）On be all provided with the second mounting hole（204-3）, the vibratory sieve weight stack（204-2）It is bolted
It is connected to the vibratory sieve sprocket wheel（204-1）On.
4. combined harvester backhaul plate according to claim 2 and vibratory sieve inertial force balancing device, it is characterised in that institute
State backhaul plate weight stack（104-2）Material is cast iron.
5. combined harvester backhaul plate according to claim 3 and vibratory sieve inertial force balancing device, it is characterised in that institute
State vibratory sieve weight stack（204-2）Material be cast iron.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201720404360.7U CN207083526U (en) | 2017-04-18 | 2017-04-18 | Combined harvester backhaul plate and vibratory sieve inertial force balancing device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201720404360.7U CN207083526U (en) | 2017-04-18 | 2017-04-18 | Combined harvester backhaul plate and vibratory sieve inertial force balancing device |
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| Publication Number | Publication Date |
|---|---|
| CN207083526U true CN207083526U (en) | 2018-03-13 |
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|---|---|---|---|
| CN201720404360.7U Expired - Fee Related CN207083526U (en) | 2017-04-18 | 2017-04-18 | Combined harvester backhaul plate and vibratory sieve inertial force balancing device |
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| Country | Link |
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| CN (1) | CN207083526U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107182452A (en) * | 2017-04-18 | 2017-09-22 | 江苏大学 | Combined harvester backhaul plate and vibratory sieve inertial force balancing device and balance method |
| CN109677722A (en) * | 2018-12-31 | 2019-04-26 | 浙江申联环保集团有限公司 | A kind of jumbo bag automatic discharge unit |
| CN111515115A (en) * | 2020-04-16 | 2020-08-11 | 武汉理工大学 | Vibrating screen conveying part of beach garbage cleaning vehicle |
-
2017
- 2017-04-18 CN CN201720404360.7U patent/CN207083526U/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107182452A (en) * | 2017-04-18 | 2017-09-22 | 江苏大学 | Combined harvester backhaul plate and vibratory sieve inertial force balancing device and balance method |
| CN109677722A (en) * | 2018-12-31 | 2019-04-26 | 浙江申联环保集团有限公司 | A kind of jumbo bag automatic discharge unit |
| CN111515115A (en) * | 2020-04-16 | 2020-08-11 | 武汉理工大学 | Vibrating screen conveying part of beach garbage cleaning vehicle |
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| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20180313 |
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| CF01 | Termination of patent right due to non-payment of annual fee |