CN109470410A - Symmetrical counterweight planetary gear train dynamic balance adjusting apparatus - Google Patents
Symmetrical counterweight planetary gear train dynamic balance adjusting apparatus Download PDFInfo
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- CN109470410A CN109470410A CN201910038236.7A CN201910038236A CN109470410A CN 109470410 A CN109470410 A CN 109470410A CN 201910038236 A CN201910038236 A CN 201910038236A CN 109470410 A CN109470410 A CN 109470410A
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- planetary gear
- gear train
- clump weight
- adjustment
- adjusting apparatus
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- 238000013461 design Methods 0.000 description 4
- 238000006243 chemical reaction Methods 0.000 description 2
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- 238000010276 construction Methods 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
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Classifications
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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
- G01M1/00—Testing static or dynamic balance of machines or structures
- G01M1/30—Compensating imbalance
- G01M1/36—Compensating imbalance by adjusting position of masses built-in the body to be tested
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Abstract
The present invention devises one kind can carry out device that is circumferential and radially adjusting to clump weight, and then the centrifugal force for the centrifugal force and entire revolving structure bias generation to be adjusted for generating clump weight bias reaches balance, to realize the dynamic balancing of entire revolution system.Dynamic balance adjusting apparatus can realize that clump weight eccentric angle arbitrarily adjusts within the scope of 360 °, it can also be achieved a certain range of adjustment in radial directions of clump weight centroid position simultaneously, the adjustment device can directly apply to the dynamic balancing adjustment of dynamic balancing adjustment in dish type revolving meber process or the little rotor structure of axial dimension during the work time.Device proposed by the present invention, mainly by be symmetrically installed counterweight block structure, for the adjustment of clump weight centroid position planetary gear train structure, the spline shaft structure of rule transformation and the tie-plate structure composition that connect with live spindle are driven for realizing planetary gear train.The present invention enormously simplifies the process of high speed rotation shafting dynamic balancing adjustment, at the same compare existing same device have the characteristics that adjust extent of the error it is big, easy to operate.
Description
Technical field
The invention belongs to rotating machinery dynamic balancing adjustment fields, it relates to one kind, and there is symmetrical counter weight construction to be based on planet
The dynamic balance adjusting apparatus of train driving.
Background technique
Either the processing of mechanical machine part still in use, all can largely encounter and need to carry out high speed rotation
The case where turning, and since the shape of workpiece blank is uneven or the error of process, it often can all cause part is practical to return
Turn not being overlapped for center and part mass center, to generate huge centrifugal load on rotating shaft, further may cause machinery
The vibration of operation process is unstable, seriously possibly even damages.Therefore, to the adjustment of rotational structure centroid position, i.e.,
Usually said dynamic balancing adjustment is all of great significance in the manufacture of rotation class mechanical equipment, assembly, using overall process.
The revolving member that need to be adjusted usually is installed on dynamic balancing machine by traditional dynamic balance adjusting method, passes through biography
Sensor, that is, respective algorithms, measurement obtain the eccentric size and eccentric direction of component, then by increase and decrease counterweight method, in corresponding position
It sets the clump weight of affixed certain mass or gets lightening hole, to change component centroid position, it is made to coincide with axis of rotation.
Conventional method it is dynamically balanced to structure adjustment be clearly present it is cumbersome, part geometry itself can be destroyed, machinery need to be set
It is standby to carry out the drawbacks such as repeated disassembled and assembled.Therefore, design a kind of device without detaching equipment, without being repaired to rotating part itself
Under conditions of changing, the dynamic balancing adjustment of rotary part can be easily realized by easily operating, will be of great significance.
Summary of the invention
The present invention designs one kind can carry out device that is circumferential and radially adjusting to clump weight, and then produce clump weight bias
The centrifugal force that raw centrifugal force and entire revolving structure bias to be adjusted generate reaches balance, to realize entire revolution system
Dynamic balancing.Dynamic balance adjusting apparatus can realize that clump weight eccentric angle arbitrarily adjusts within the scope of 360 °, can also be achieved simultaneously
The a certain range of adjustment in radial directions of clump weight centroid position, it is processed which can directly apply to revolving meber
The dynamic balancing adjustment of dynamic balancing adjustment or rotary axis during the work time in journey.
The present invention proposes the dynamic balance adjusting apparatus based on planetary gear train and spline shaft structure to realize the above-mentioned technical purpose
Design, which can fast implement axial dimension less and the dynamic balancing adjustment of eccentric larger rotor structure, it mainly by
The counterweight block structure that is symmetrically installed, for the planetary gear train structure of clump weight centroid position adjustment, for realizing planetary gear train biography
The spline shaft structure of dynamic rule transformation and the tie-plate structure composition being connect with live spindle.
The main function of counterweight block structure is that the mass center of dynamic balance adjusting apparatus and axis of rotation is made to generate certain bias,
To uneven to balance rotational structure bias bring to be adjusted.
The main function of planetary gear train is, with certain transmission ratio, to realize peace in the case where input shaft has rotation to drive
The reversed and rotating Vortex of the pairs of clump weight on train output shaft, and then it is implemented as the diameter to clump weight mass center
To and circumferential adjustment.
Spline shaft structure runs through the axle center of the planetary gear train, by pressing mentioned-above button, it can be achieved that splined shaft
Axial position adjustment, complete three kinds of drive states of planetary gear train between conversion.
Tie-plate makes dynamic balance adjusting apparatus with wait adjust for dynamic balance adjusting apparatus and rotary main shaft to be assembled together
Whole rotary part synchronous rotary.
Compared to existing dynamic balance adjusting method and device, the invention has the following advantages that
1) revolving-body dynamic-balancing adjustment is carried out using the dynamic balance adjusting apparatus, weld counterweight block can be removed from and got subtracts
The troublesome operation of repeated hole, and can adjust repeatedly at any time.It is easier compared to traditional dynamic balance adjusting method, and will not destroy
Part script structure.
2) it is based on planetary gear train structure, the radial direction and circumferential adjustment of clump weight can be realized by single rotation process, because
This scale that can directly read calibration is adjusted, and is eliminated some other dynamic balance adjusting apparatus and is counted to clump weight position
The step of calculating with measurement；Rotation process single simultaneously is also convenient for realizing by motor and automatically control.
3) the dynamic balance adjusting apparatus clump weight has larger quality and bias, the dress for passing through threaded adjustment compared to many
It sets, it can be achieved that large range of dynamic balancing adjustment.
4) splined shaft is matched with spring structure, it can be achieved that clump weight position in normal operation locks automatically,
Therefore additional fixation is not necessarily to clump weight, also further simplifies the process of dynamic balancing adjustment.
Detailed description of the invention
Fig. 1 is dynamic balance adjusting apparatus entirety assembling schematic diagram
Fig. 2 is dynamic balance adjusting apparatus appearance schematic diagram
Fig. 3 is clump weight appearance schematic diagram
Fig. 4 is symmetrical counterweight assembling form schematic diagram
Fig. 5 is counterweight adjustment mode schematic diagram
Fig. 6 is lock state planetary gear train structure diagram
Fig. 7 is radial adjustment state planetary gear train structure diagram
Fig. 8 is circumferential adjustment state planetary gear train structure diagram
Fig. 9 is splined shaft appearance schematic diagram
Figure 10 is lock state splined shaft meshing relation schematic diagram
Figure 11 is radial adjustment state splined shaft meshing relation schematic diagram
Figure 12 is circumferential adjustment state splined shaft meshing relation schematic diagram
Figure 13 is tie-plate appearance schematic diagram
Figure 14 is tie-plate structure sectional view
Wherein, 1 is button, with spline axis connection for adjusting splined shaft axial position；2 be knob, is connected with planetary gear train
It connects, for train movement input；3 be planetary gear 5 '；4 be planet carrier H2, is train motion inlet shaft；5 be planetary gear 5；Centered on 6
Wheel 3；7 be planetary gear 2 '；8 be clump weight 2, while being also planet carrier H1, is train movement output axis 2；9 be planetary gear 2；10 are
Clump weight 1, while being also centre wheel 1, it is train movement output axis 1；11 be rack；12 be tie-plate；13 be female splined shaft；14
For male splined shaft.
Specific embodiment
It is as shown in Figure 1 symmetrical counterweight planetary gear train dynamic balance adjusting apparatus entirety sectional arrangement drawing, it is mainly by symmetrical
Four counterweight block structure, planetary gear train adjustment structure, spline shaft adjusting structure, connection dish structure parts form.Wherein, Fig. 1 institute
Show 1 for button, with spline axis connection for adjusting splined shaft axial position；2 be knob, is connect with planetary gear train, is transported for train
Dynamic input；3 be planetary gear 5 '；4 be planet carrier H2, is train motion inlet shaft；5 be planetary gear 5；3 are taken turns centered on 6；7 be planet
Wheel 2 '；8 be clump weight 2, while being also planet carrier H1, is train movement output axis 2；9 be planetary gear 2；10 be clump weight 1, together
When be also centre wheel 1, be train movement output axis 1；11 be rack；12 be tie-plate；13 be female splined shaft；14 be external splines
Axis.
It is illustrated in figure 2 the positive isometric view of symmetrical counterweight planetary gear train dynamic balance adjusting apparatus.
First part illustrates counterweight block structure and installation form first:
Clump weight uses in pairs, and two pairs of counterweights are block-shaped, size is identical, their structure as shown in figure 3,
Outer profile is disc, and wherein half is solid, the other half is the hollow structure supported by floor, so their installation
Center, i.e., the centre of gyration rotated with main shaft, is not just overlapped, there are certain eccentric distances between mass center.When pairs of is matched
When pouring weight mass center is symmetrically installed about the centre of gyration, as shown, the common mass center of two pairs of clump weights just and the centre of gyration
It is overlapped, entire dynamic balance adjusting apparatus is in equilibrium state at this time.Wherein, A, B are respectively the mass center of two clump weights, O two
The installation center of clump weight.
The radial adjustment mode of clump weight mass center:
After pairs of clump weight reversely angularly rotates the angle θ, as shown in figure 4, the common mass center of two clump weights and installation
Center will not be overlapped, and produce certain bias, offset distance e, then relationship between offset distance and corner are as follows:
E=R0sinθ
Wherein, R0For the setting-up eccentricity of clump weight；
The circumferential adjustment mode of clump weight mass center:
When two clump weights angularly rotate in the same direction, as shown in figure 5, eccentric angle will change, change angle
Degree is rotation angle, i.e. the angle α in Fig. 5.
Second part illustrates planetary gear train structure and its characteristics of motion:
It realizes the angularly in the same direction of two output shafts and reversely rotates function, then the planetary gear train structure such as Fig. 6 designed,
7, shown in 8, the planetary gear train is altogether there are three types of working condition, and the conversion between three kinds of working conditions is by the subsequent spline shaft structure
It realizes.The wheel ties up under three kinds of states the reverse rotation of the locking and two output shafts that can realize train movement respectively, rotation in the same direction
Rotating function.Wherein, planet carrier H2 is movement input, and planet carrier H1 is movement output 1, and gear 1 is movement output 2.Separately below
Input and output movement relation of the planetary gear train under three kinds of states is illustrated:
1) under state shown in Fig. 6, planet carrier H2 and gear 4 and rack are affixed, because planet carrier H2 is movement input, if
Affixed with rack, then input shaft can not rotate, and be motion locking state.
2) under state shown in Fig. 7, gear 3 and gear 4 and rack are affixed, and mechanism can be divided into two planetary gear trains and be divided
Analysis.For the train that left side is made of gear 4, gear 5, gear 5 ', gear 6, planet carrier H2, in change train underdrive ratio
Are as follows:
Wherein, Z4It is 78 for 4 number of teeth of gear；Z5It is 28 for 5 number of teeth of gear；Z5’It is 30 for the 5 ' number of teeth of gear；Z6For tooth
6 numbers of teeth are taken turns, are 80；ω4It since gear 4 and rack are affixed, therefore is 0 for 4 angular speed of gear；
Transmission ratio, which can be calculated, by known parameters is
Gear 6 and planet carrier 1 are affixed, i.e., the reduction ratio of movement output 1 is 22.4.
For the train that right side is made of gear 1, gear 2, gear 2 ', gear 3, planet carrier H1, passed under change train
Dynamic ratio is
Wherein, Z1It is 30 for 1 number of teeth of gear；Z2It is 30 for 2 number of teeth of gear；Z2’It is 20 for the 2 ' number of teeth of gear；Z3For tooth
3 numbers of teeth are taken turns, are 40；ω3It since gear 3 and rack are affixed, therefore is 0 for 3 angular speed of gear；
Therefore transmission ratio can be calculated by known parameters and be
Planet carrier H1 be movement output 1, gear 1 be movement output 2, therefore by transmission ratio as it can be seen that the two direction of motion on the contrary,
Corner size is identical.
3) in the state shown in fig. 8, gear 3 and planet carrier H1 are affixed, and gear 4 and rack are affixed, therefore left side planet
Train with 2) described in situation it is identical, transmission ratio is still 22.4；And right side gear gear 3 is identical as planet carrier H1 angular speed, i.e.,
ωH=ω3, it is updated in change train transmission ratio formula, has
Therefore train freedom degree is 0, can not be rotated, therefore gear 1 and planet carrier H2 is equivalent to affixed, movement output 1
It is identical as 2 direction of movement output, corner is equal.
Part III illustrates the function and implementation of spline shaft structure:
It is corresponding on axis when splined shaft being needed to be in different location for the purpose for realizing converting planet train drive state
Spline is meshed from different gears or planet carrier or rack, and design spline shaft structure is as shown in Figure 9.Splined shaft be divided into inner shaft with
It two layers of outer shaft, can relatively rotate between inside and outside axis, the spline and each central gear, planet under three kinds of positions, on splined shaft
Meshing relation between frame, rack is illustrated separately below:
1) as shown in Figure 10, for splined shaft in left-most position, planet carrier H2, gear 4 are solid by male splined shaft and rack
It connects, corresponding to planetary gear train at this time is motion locking state；
2) as shown in figure 11, splined shaft moves right the distance of a transverse tooth thickness, the i.e. distance of 4mm, and gear 4 and gear 3 are logical
It is affixed with rack to cross male splined shaft, planet carrier H2 is connect with female splined shaft, and female splined shaft is not affixed with rack at this time, can freely be turned
It is dynamic, the reverse rotation state of two output shaft of planetary gear train is corresponded at this time.
3) as shown in figure 12, gear 4 is affixed by female splined shaft and rack, and gear 3, planet carrier H1 and male splined shaft connect
It connects, male splined shaft is not affixed free to rotate with rack at this time, corresponds to the rotating Vortex state of two output shaft of planetary gear train at this time.
Part IV illustrates the structure of tie-plate and its connecting mode with rotary axis:
As shown in figure 13 be tie-plate outline drawing, dynamic balance adjusting apparatus main body by center M22 threaded hole with couple
Disk axial restraint, it is circumferentially fixed using holding screw realization by flank threads hole；Main shaft is connected with tie-plate lower end.
As shown in figure 14 it is tie-plate cross-sectional view, key dimension is labelled in figure, lower end location hole has certain taper, on
Counter sink there are four opening is held, it can be affixed by four 10 screws of Φ and main shaft.Tie-plate meets GB/T with the size that couples of main shaft
5900.1-2008 standard.
The example of embodiment described above, the only present invention to explain its function, it is intended that help this field
Technical staff understands core of the invention thought, and non-present invention feasibility embodiment is unique.It should be pointed out that for this skill
For the ordinary person in art field, under the premise of not departing from the principle of the invention and spirit, the present invention can also be carried out related
Improvement and modification, these improvement and modification should all be contemplated as falling within claims of the invention.
Claims (4)
1. symmetrical counterweight planetary gear train dynamic balance adjusting apparatus, which is characterized in that comprising be symmetrically installed counterweight block structure, driving
The planetary gear train structure of clump weight rotation, the spline shaft structure for realizing planetary gear train transmission rule variation are realized with rotary axis
The connection dish structure of connection.
2. symmetrical counterweight planetary gear train dynamic balance adjusting apparatus as described in claim 1, which is characterized in that the symmetrical peace
The counterweight of dress is divided into full symmetric two parts clump weight, and two parts clump weight installation center is not overlapped with mass center,
Two parts clump weight is by can be achieved the common matter of two parts clump weight around the in the same direction of installation center and reverse rotation
The radial direction of heart position and circumferential adjustment.
3. symmetrical counterweight planetary gear train dynamic balance adjusting apparatus as described in claim 1, which is characterized in that the planetary gear
Architecture has a motion inlet shaft and two movement output axis, and there are three types of be driven shape for the planetary gear train structure tool
The motion locking, angularly same of two movement output axis may be implemented in state respectively under three kinds of drive states
To rotation, angularly reversely rotate.
4. symmetrical counterweight planetary gear train dynamic balance adjusting apparatus as described in claim 1, which is characterized in that the splined shaft
Structure has female splined shaft, male splined shaft double-layer structure, and can relatively rotate between the double-layer structure, while the interior flower
Key axis and male splined shaft are axially movable and the central gear and planet carrier three kinds of differences of formation in the planetary gear train structure
Meshing state.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201910038236.7A CN109470410A (en) | 2019-01-14 | 2019-01-14 | Symmetrical counterweight planetary gear train dynamic balance adjusting apparatus |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910038236.7A CN109470410A (en) | 2019-01-14 | 2019-01-14 | Symmetrical counterweight planetary gear train dynamic balance adjusting apparatus |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112338215A (en) * | 2020-11-10 | 2021-02-09 | 井冈山大学 | High-speed main shaft convenient to realize secondary dynamic balance |
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| EP0992781A2 (en) * | 1998-10-08 | 2000-04-12 | BalaDyne Corporation | Balancer |
| WO2001008807A1 (en) * | 1999-08-03 | 2001-02-08 | Eppendorf Ag | Imbalance compensation device for centrifuges |
| CN2584939Y (en) * | 2002-11-21 | 2003-11-05 | 洛阳轴研科技股份有限公司 | Cylindrical grinding machine contactless driving type grinding wheel balance device |
| CN1647764A (en) * | 2004-01-28 | 2005-08-03 | 西门子公司 | Imaging fault contrast device |
| US20080302181A1 (en) * | 2004-07-27 | 2008-12-11 | Franz Haimer Machinenbau Kg | Balance Ring and Method For Balancing a Rotating Component |
| DE102012100782A1 (en) * | 2012-01-31 | 2013-08-01 | Hofmann Mess- Und Auswuchttechnik Gmbh & Co. Kg | Apparatus and method for balancing rotors |
| CN105241608A (en) * | 2015-10-13 | 2016-01-13 | 沈阳建筑大学 | Built-in electromagnetic drive type dynamic balance apparatus for main shaft |
| CN108134537A (en) * | 2018-01-09 | 2018-06-08 | 西安交通大学 | A kind of built-in piezo-electric type on-line dynamic balancing executive device |
| CN108534952A (en) * | 2017-03-01 | 2018-09-14 | 宜昌长机科技有限责任公司 | A kind of device of automatic adjustment dynamic balancing |
| CN108956015A (en) * | 2018-09-26 | 2018-12-07 | 华侨大学 | Electromagnetic type on-line dynamic balancing system |
-
2019
- 2019-01-14 CN CN201910038236.7A patent/CN109470410A/en active Pending
Patent Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0992781A2 (en) * | 1998-10-08 | 2000-04-12 | BalaDyne Corporation | Balancer |
| WO2001008807A1 (en) * | 1999-08-03 | 2001-02-08 | Eppendorf Ag | Imbalance compensation device for centrifuges |
| CN2584939Y (en) * | 2002-11-21 | 2003-11-05 | 洛阳轴研科技股份有限公司 | Cylindrical grinding machine contactless driving type grinding wheel balance device |
| CN1647764A (en) * | 2004-01-28 | 2005-08-03 | 西门子公司 | Imaging fault contrast device |
| US20080302181A1 (en) * | 2004-07-27 | 2008-12-11 | Franz Haimer Machinenbau Kg | Balance Ring and Method For Balancing a Rotating Component |
| DE102012100782A1 (en) * | 2012-01-31 | 2013-08-01 | Hofmann Mess- Und Auswuchttechnik Gmbh & Co. Kg | Apparatus and method for balancing rotors |
| CN105241608A (en) * | 2015-10-13 | 2016-01-13 | 沈阳建筑大学 | Built-in electromagnetic drive type dynamic balance apparatus for main shaft |
| CN108534952A (en) * | 2017-03-01 | 2018-09-14 | 宜昌长机科技有限责任公司 | A kind of device of automatic adjustment dynamic balancing |
| CN108134537A (en) * | 2018-01-09 | 2018-06-08 | 西安交通大学 | A kind of built-in piezo-electric type on-line dynamic balancing executive device |
| CN108956015A (en) * | 2018-09-26 | 2018-12-07 | 华侨大学 | Electromagnetic type on-line dynamic balancing system |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112338215A (en) * | 2020-11-10 | 2021-02-09 | 井冈山大学 | High-speed main shaft convenient to realize secondary dynamic balance |
| CN112338215B (en) * | 2020-11-10 | 2024-05-03 | 井冈山大学 | High-speed main shaft adjusting method convenient for realizing secondary dynamic balance |
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