CN2329809Y - Self-regulating constant force disc spring supporting hanger - Google Patents
Self-regulating constant force disc spring supporting hanger Download PDFInfo
- Publication number
- CN2329809Y CN2329809Y CN 98225867 CN98225867U CN2329809Y CN 2329809 Y CN2329809 Y CN 2329809Y CN 98225867 CN98225867 CN 98225867 CN 98225867 U CN98225867 U CN 98225867U CN 2329809 Y CN2329809 Y CN 2329809Y
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- fixed
- dish spring
- frame
- main shaft
- disc spring
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Abstract
The utility model relates to a self-adjusting constant force disc spring hanger, comprising a fixed frame, a rotating frame, a disc spring group, etc. The utility model is characterized in that the revolving frame which is fixed on the fixed frame by a spindle can rotate around the spindle; a loading shaft, a pull rod shaft, a pull rod connecting pull piece shaft, and a disc spring pressing plate in the disc spring group are arranged on the revolving frame; the disc spring group is fixed by a spherical shaft head which is fixed in a spherical bearing of the side wall of the fixed frame; the rotating frame which rotates around the spindle can generate the rotation of 90 DEG. The utility model which has the advantages of compact structure, small size, large range of displacement, and high utilization rate of disc springs can be widely used for equipment which easily generates deformation stress, such as boilers, power generation, petrochemical industries, metallurgy, electrified railroad contact lines, etc.
Description
The utility model relates to a kind of disc spring bearing hanger.
Present disc spring bearing hanger, its design be with the turning circle week of the pull bar of dish spring and slewing frame tangent, one section revolution of getting near linear is about to the operating range of the akin displacement region of dish spring force of cumulative property pull bar rotating force arm and cumulative property as constant hanger apart from making its work distance.Therefore, the fixed frame weldering that shows as dished spring assembly and suspension and support on product structure is one, dish spring pull bar is defined to the straight-line displacement mode, and the starting point of rotating force arm ends at a shaft horizontal line above the horizontal line of fulcrum and the angle at 45 with the horizontal line of fulcrum.Therefore this structure rotating force arm is long, and mechanism's volume is bigger, is in 4 ° the drift angle scope for guaranteeing constant supporting spring hanger and suspension, and the vertical space of its suspension bracket requires greatly.Produce the suspension and support of 400mm vertical displacement as present load axle, the long 565mm of its revolution pull bar, load axle horizontal displacement 165mm reaches 41% with the ratio of vertical displacement amount.Simultaneously, because its designing requirement has the near linear displacement, caused and selected for use the displacement amount of dish spring little, magnification factor to mechanism is bigger, again because the characteristic curve of the characteristic curve of mechanism and dish spring is non-identical, thus lower to the utilization ratio of dish spring, be generally about 75%.And same displacement suspension bracket be because the difference of load just can't be used with a kind of dish spring, and load is identical equally, and the displacement difference can not be used with a kind of dish spring, causes the dish spring various in style, and interchangeability is poor, is difficult to batch process and standardization, seriation.
The purpose of this utility model provides the self-regualting type constant-force disk spring support hanger that a kind of volume is little, rotary displacement big, dish spring utilization ratio is high.
The purpose of this utility model realizes by following technical solution:
Self-regualting type constant-force disk spring support hanger described in the utility model comprises fixed frame, slewing frame, dish spring group etc., be characterized in that slewing frame fixes by a main shaft and fixed frame, and slewing frame can be around this main shaft gyration; Be fixed with a load axle on the slewing frame, a pull rod shaft; On the corresponding sidewall of fixed frame and pull rod shaft ball bearing is housed, the spherical spindle nose of spherical axle is loaded in this ball bearing, and the other end is fixed on the dish spring group sidewall; In the dish spring group dish spring is housed, a pressing plate is housed on the dish spring; One end of pull bar is fixed on the pull rod shaft, and the other end is fixed on the dish spring pressing plate.Slewing frame is when main shaft gyration, and the axial connecting line of its load axle and main shaft can produce along the axle center horizontal plane of main shaft along this horizontal plane upwards 45 ° or downward 45 ° angle of revolution.
The utility model has the advantages that compact structure, volume are little, displacement range is big, the utilization ratio height of dish spring.Can extensively be suitable for the equipment that boiler, generating, petrochemical industry, metallurgy, electrification railway contact net etc. easily produce deformational stress.
Below in conjunction with an embodiment the technical solution of the utility model is described further:
What Fig. 1 provided is agent structure schematic representation of the present utility model;
What Fig. 2 provided is working state schematic representation of the present utility model;
Fig. 3 is the performance diagram of dish spring;
Fig. 4 is a pull bar gyroscopic characteristics plotted curve;
Fig. 5 is a slewing frame working status parameter graph of a relation.
In Fig. 1, the 1st, fixed frame of the present utility model, the 10th, slewing frame is provided with a main shaft 8 on this slewing frame, and this main shaft 8 is fixed on slewing frame 10 on the fixed frame 1, and slewing frame 10 is rotated around this main shaft.Also be fixed with a load axle 2 on the slewing frame 10, to prop weight (as boiler etc.) W that is suspended; Also establish a pull rod shaft 3 on the slewing frame 10.Fixed frame 1 with pull rod shaft 3 respective side walls on fixing ball bearing 11, the spherical spindle nose of spherical axle 5 is positioned at ball bearing 11, the other end is fixed on the sidewall of dish spring group 7, establishes some dish springs 6 in the dish spring group, and pressing plate 12 is housed on the dish spring 6; Pull bar 4 one ends are fixed on the pull rod shaft 3, and an end is fixed on the dish spring pressing plate 12.Be original state of the present utility model when slewing frame 10 is in shown position, satisfy following designing requirement this moment: 1. to become angle α with the line AC of the axle center C of load axle 2 with the axle center horizontal plane of main shaft be 45 ° to the axle center A of main shaft 8; 2. the line BD of the spherical spindle nose center D of the axle center B of pull rod shaft and spherical axle is located in the same horizontal plane, and with the axis of pull bar 4, dish spring group 7 in same horizontal plane.If A hands over BD in the E point to the vertical line of BD, then AE is pull bar 4 around main shaft 8 rotating rotating force arms.If the horizontal line vertical line intersection point that C is ordered to A is K, then AK is that load axle 2 is around the main shaft 8 rotating arm of forces.
It is as follows that the utility model realizes that the self-regulating constant force is propped up the working principle of hanging:
As shown in Figure 2, when the utility model props up the weight that hangs and produces deformation for a certain reason (as boiler because be heated bulk expansion or cooling overall shrinkage etc.), if this moment is because deformation weight W produces downward displacement, then slewing frame 10 generations are around the revolution of main shaft 8, and wherein pull rod shaft 3 will be the radius edge with AB
Circular arc revolution, load axle be radius with AC around
The camber line revolution.If the position after the revolution as shown in phantom in FIG., promptly B is turned back to B ', and C is turned back to C '.The load axle is β around the angle of revolution of main shaft.Establish this displacement vertical displacement BF for to B order because pull bar 4 produces displacement this moment, and then pull bar will drive pressing plate 12 compact disc springs 6, makes dish spring 6 produce elastic strain.Because the elastically-deformable generation of dish spring 6, the dish spring will produce elastic-restoring force and act on pull bar, so the stressed of pull bar will change, than the stressed increase of initial position.This moment, spherical 5 spherical spindle nose produced rotation upwards simultaneously, and for guaranteeing the stressed all the time along its axial direction of pull bar, spherical 5 spindle nose sphere is necessary for the sphere more than or equal to hemisphere.The arm of force of pull bar 4 will change as shown in Figure 2 this moment, become AE ' by the AE of initial position, and the arm of force of load axle 2 also changes, and becomes AK ' by initial AK.After the parameter of selected AC, AB, CB, BD, AD, pull bar length, suitably choose the parameter of dish spring, can calculate stressed stressed with the load axle of pull bar according to principle of moment balance, can calculate in view of the above because the load axle that the deformation of load W causes stressed.According to each point load axle stressing conditions when the difference of slewing frame rotary position, can calculate the stressed invariance degree of load axle.This shows that the load axle depends on the parameter of physical dimension, pull rod shaft and spherical axle spindle nose centre of sphere size, pull bar length and dish spring between load axle, main shaft, the pull rod shaft three around the angle of revolution of main shaft scope.Suitably choose above-mentioned parameter and can realize the load axle, and the self-regulating constant force that realizes suspension bracket is propped up and hung around the revolution of 45 ° of scopes up or down of spindle axis horizontal plane.The constant-force disk spring support hanger that now with the load rating is 4350KG is that example is calculated as follows: the axle base AC=141.1mm that 1. chooses slewing frame main shaft and load axle, the distance between shafts AB=102.43mm of main shaft and pull rod shaft, main shaft arrives the spindle nose centre of sphere of spherical axle apart from AD=180.28mm, the spherical axle spindle nose centre of sphere is arrived apart from BD=127.8mm in the pull bar axle center, the axial connecting line CB of pull rod shaft and load axle and with the angle of the axial connecting line CA of main shaft be ∠ CAB=45 °, on the same horizontal plane in CBD place.Be original state this moment, can calculate AE=100mm, CK=100mm (referring to Fig. 1).2. be that the stressed dish reed of 10KG is formed dish spring 6 after selection standard flattens, making its decrement coefficients R is 0.25,0.5,0.54,0.75 o'clock, and it is stressed to be 4350KG, 6500KG, 6900KG, 8500KG.The characteristic curve of promptly choosing the dish spring as shown in Figure 3.Then have: when the load axle is turned back to C, C ', C ", C " ' during one of four states as shown in Figure 5, corresponding to: (a) dish spring decrement coefficient is 0.25 o'clock, stressed 4350KG, pull bar displacement this moment is zero, be BF=0, AE=100mm, AK=100mm; It is initial state; (b) dish spring decrement coefficient is 0.5 o'clock, stressed is 6500KG, pull bar displacement this moment BF '=67mm, AE '=93.9mm, AK '=140mm:(c) dish spring decrement coefficient is 0.54 o'clock, stressed 6900KG, pull bar displacement BF "=77.7mm; AE "=89.9mm, AK at this moment "=141mm; The displacement of load axle horizontal reaches maximum value; (d) dish spring decrement coefficient is 0.75 o'clock, stressed 8500KG, pull bar displacement this moment BF =135mm, AE =50.9mm, AK =100mm;
The relation curve that provides pull bar arm of force AE value and dish spring according to above-mentioned four kinds of states as shown in Figure 4, this is the pull bar gyroscopic characteristics curve of slewing frame.
Provide its corresponding working state parameters relationship as shown in Figure 5 according to above-mentioned four kinds of states.
According to above-mentioned four kinds of states, utilize principle of moment balance, calculate stressed following (the establishing the stressed N of being of load axle) of load axle respectively:
Because N=dish spring is stressed * arm of force (AE)/load axle arm of force (AK), (because the dish spring is stressed for elastic-restoring force equals the pulling force of pull bar, the stressed decrement coefficient that equals of dish spring multiply by pressure).
So: to (a), 4350 * 100/100=4350KG during N=0.25;
To (b), 6500 * 93.9/140=4360KG during N=0.50;
To (c), 6900 * 89.8/141=4384KG during N=0.54;
To (d), 8500 * 50.9/100=4326KG during N=0.75.
So, the invariance degree of this constant force disc spring hanger=(maximum value-minimum value)/(maximum value+minimum value)=(4384-4326)/(4384+4326)=0.67% therefore, its invariance degree is better than 6% standard-required greatly.And the load axle than the maximum horizontal displacement amount of initial state is in this suspension bracket operation process: (141mm-100mm)=41mm, can calculate its swing drift angle less than 4 ° requirement.Owing to the expansion of dish spring selection of parameter scope, improve the utilization ratio of dish spring greatly simultaneously, can reach 95%, can save material.Choose parameter according to above-mentioned design principle, produce the suspension bracket of 400mm vertical displacement for present load axle, can make its pull bar length dwindle half than originally, be 283mm, the displacement of load axle horizontal was dwindled half than originally, was 83mm, and vertical displacement is reduced into 20.5% than originally, thereby its volume greatly reduces, and can make the load axle produce 90 ° of revolutions.Not only performance improves, and can save lot of materials.
Claims (3)
1. the self-regualting type constant-force disk spring support hanger comprises fixed frame (1), slewing frame (10), dish spring group (7), it is characterized in that slewing frame (10) is fixed on fixed frame (1) by a main shaft (8) and goes up and can turn round around this main shaft (8); Also be fixed with a load axle (2) on this slewing frame (10), a pull rod shaft (3); Fixed frame (1) is equipped with ball bearing (11) on the sidewall accordingly with pull rod shaft (3), and the spherical spindle nose of spherical axle (5) is contained in this ball bearing (11), and the other end is fixed on dish spring group (7) sidewall; Dish spring (6) is housed in the dish spring group (7), pressing plate (12) is housed on the dish spring (6); One end of pull bar (4) is fixed on the pull rod shaft (3), and the other end is fixed on the dish spring pressing plate (1 2); When slewing frame (10) turned round around main shaft (8), the axial connecting line of its load axle (2) and main shaft (8) can produce along the axle center horizontal plane of main shaft (8) along this horizontal plane angle of revolution of 45 ° up or down.
2. the suspension and support described according to claim is characterized in that the spherical spindle nose of described spherical axle (5) is the sphere more than or equal to hemisphere.
3. suspension and support according to claim 1 and 2 is characterized in that the decrement coefficient of its corresponding dish spring (6) is greater than its central value 0.50 when slewing frame (10) produces maximum horizontal displacement.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 98225867 CN2329809Y (en) | 1998-01-21 | 1998-01-21 | Self-regulating constant force disc spring supporting hanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 98225867 CN2329809Y (en) | 1998-01-21 | 1998-01-21 | Self-regulating constant force disc spring supporting hanger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2329809Y true CN2329809Y (en) | 1999-07-21 |
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ID=33976474
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 98225867 Expired - Fee Related CN2329809Y (en) | 1998-01-21 | 1998-01-21 | Self-regulating constant force disc spring supporting hanger |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN2329809Y (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107101082A (en) * | 2017-05-31 | 2017-08-29 | 北京若贝特智能机器人科技有限公司 | A kind of spring supporting device |
-
1998
- 1998-01-21 CN CN 98225867 patent/CN2329809Y/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107101082A (en) * | 2017-05-31 | 2017-08-29 | 北京若贝特智能机器人科技有限公司 | A kind of spring supporting device |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C19 | Lapse of patent right due to non-payment of the annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |