CN210371655U - Supporting device and anti-seismic device applying same - Google Patents
Supporting device and anti-seismic device applying same Download PDFInfo
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- CN210371655U CN210371655U CN201920613496.8U CN201920613496U CN210371655U CN 210371655 U CN210371655 U CN 210371655U CN 201920613496 U CN201920613496 U CN 201920613496U CN 210371655 U CN210371655 U CN 210371655U
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Abstract
The utility model discloses a strutting arrangement and applied strutting arrangement's antidetonation device, including radial bearing, radial bearing cup joints the interior anchor clamps of spring outward, and the anchor clamps cup joints the outer anchor clamps of first spring outward in the spring, is provided with first oblique coil spring between anchor clamps and the outer anchor clamps of first spring in the spring. The rotating shaft is sleeved with the supporting device. When the slender rotating shaft rotates automatically, the supporting device can effectively compensate the radial offset distance of the slender rotating shaft in any direction and other installation errors.
Description
Technical Field
The utility model belongs to the technical field of transmission, a strutting arrangement is related to, still relate to an use above-mentioned strutting arrangement's antidetonation device.
Background
The industrial center shaft has extremely wide application, wherein the shock absorption and shock isolation of the center shaft are the problems that the center of the shaft needs to be solved in the application, particularly, the slender shaft and the slender rotating shaft have poor rigidity, can generate obvious radial deformation under high-speed self-rotation, increase the eccentricity of the shaft, influence the normal work of the shaft, and even have instability under certain severe conditions; in addition, whether the slender shaft can be accurately and quickly centered under the condition of vibration or impact is also a key technical problem, and the solution of the problems has important significance on the stability and reliability of the shaft under the industrial production or practical application; similarly, when the slender cylindrical rod piece is subjected to impact load, the impact part of the rod piece can be severely deformed, and the excitation caused by the impact directly or indirectly influences the normal work of other connecting parts.
To solve the problems, some slender shaft transmission systems (or coupling systems) adopt an over-constraint method to add a fixed support to the middle part of the slender shaft, the fixed support can limit the rotation offset deformation of the middle part of the shaft, but due to the fact that the axial length of the slender shaft is too long, the over-constraint cannot guarantee the coaxiality of fixed support points, the normal work of the shaft is greatly influenced, even severe abrasion or bending can occur, and the service life of the shaft is shortened (the slender cylindrical rod piece is also suitable).
There is no simple and effective solution to this current market, and existing solutions such as the circular arrangement of linear springs, or the use of constant force springs, etc., all suffer from one or more of the following problems: (1) the common straight-line positive coil spiral spring can only be used as an energy accumulator to store energy, cannot slowly release the energy, and needs to be additionally provided with a corresponding variable transmission ratio mechanism to serve as a damping device; (2) the common straight-line positive coil spring cannot ensure normal work under large-range flexibility deviation in the vertical axial direction, cannot keep the elasticity in an approximately constant state, has large elasticity change in the application process and is easy to lose efficacy; (3) the existing structure can not make most of the outer diameter of the shaft contact and bear force, and can not compensate the combination error and the uneven surface of the shaft surface under certain special application environments.
SUMMERY OF THE UTILITY MODEL
The utility model aims at providing a strutting arrangement can realize the automatic centering function of the transmission shaft that supports when accomplishing the support function.
The utility model provides a technical scheme be, a strutting arrangement, including radial bearing, radial bearing has cup jointed the interior anchor clamps of spring outward, and the anchor clamps overcoat has cup jointed the outer anchor clamps of first spring in the spring, is provided with first oblique coil spring between anchor clamps in the spring and the outer anchor clamps of first spring.
The utility model discloses a characteristics still lie in:
a first groove is formed in the circumference of the outer surface of the spring inner clamp, and the inclined ring spring is located in the first groove.
The first groove a is formed along the circumference of the outer surface of the spring inner clamp, the second groove matched with the first groove a is formed along the circumference of the inner surface of the first spring outer clamp, and the first inclined ring spring is positioned in a cavity formed by the first groove a and the second groove.
The first spring outer clamp is sleeved with a second spring outer clamp, a second inclined coil spring is arranged between the first spring outer clamp and the second spring outer clamp, and the inclination angles of the first inclined coil spring and the second inclined coil spring are opposite in direction.
The first spring outer clamp is provided with a first groove along the outer surface circumference of the first spring, the second spring outer clamp is provided with a second groove along the inner surface circumference of the second spring, the second groove is matched with the first groove, and the second inclined ring spring is positioned in a cavity formed by the first groove and the second groove.
The third groove is symmetrical to the second groove; the first groove a and the fourth groove are symmetrical.
Another object of the utility model is to provide an use strutting arrangement's antidetonation device can play the effect of shock attenuation buffering and compensation radial displacement.
The utility model discloses another kind of adopted technical scheme is, an use strutting arrangement's antidetonation device, including the pivot, cup jointed above-mentioned strutting arrangement in the pivot.
The rotating shaft is a slender rotating shaft, and the radial bearing is positioned at the midpoint of the rotating shaft.
The supporting devices comprise a plurality of supporting devices, and each supporting device is uniformly distributed at a point which generates a large offset distance when the rotating shaft rotates.
The deflection angle of the first inclined coil spring and the second inclined coil spring in the winding process is equal to the taper angle of the conical surface of the slender rotating shaft.
The utility model has the advantages that: the inclined ring spring with the annular structure between the spring inner clamp and the first spring outer clamp of the supporting device of the utility model can bear compression deformation, has good return performance, can still ensure normal work under impact, vibration and severe environment, and has simple structure; the annular inclined ring spring can realize the function of automatic centering; the spring can work normally under the large range of flexible deviation, the elasticity is almost constant, and the spring does not deform too much; the utility model discloses an anti-seismic device of applied strutting arrangement, the structure of oblique circle spring is special, and its contact point is arranged almost continuously, and single coil individual atress takes place to warp, can compensate under the special application environment combination tolerance and the surface unevenness of axle surface; when the slender rotating shaft rotates automatically, the supporting device can effectively compensate the radial offset distance of the slender rotating shaft in any direction and other installation errors, and the like, and plays roles in damping, buffering and compensating radial displacement.
Drawings
Fig. 1 is a schematic structural view of a supporting device of the present invention;
fig. 2 is a schematic structural view of an inner spring clamp of a supporting device according to the present invention;
fig. 3 is a cross-sectional view of a support device of the present invention;
fig. 4 is a schematic structural view of another embodiment of a support device of the present invention;
fig. 5 is a schematic structural view of an anti-seismic device using a supporting device according to the present invention;
fig. 6 is an operation state diagram of an anti-seismic device using a supporting device according to the present invention;
fig. 7 is an operation state diagram of an anti-seismic device using a supporting device according to the present invention;
fig. 8 is a schematic structural view of another embodiment of the anti-seismic device using the supporting device of the present invention;
fig. 9 is a schematic view of a series structure of an anti-seismic device using a supporting device according to the present invention;
fig. 10 is a force analysis diagram of a single-turn inclined-coil spring of an anti-seismic device using a supporting device according to the present invention;
fig. 11 is a force analysis diagram of a single-ring inclined-ring spring of an anti-seismic device using a supporting device according to the present invention;
FIG. 12 is a force deformation diagram of a full-circle canted-coil spring of an anti-seismic device employing a support device according to the present invention;
fig. 13 is a deformation diagram of the contact point of the single-turn inclined-coil spring of the anti-seismic device using the supporting device of the present invention.
In the figure, 1 is a radial bearing, 2 is a spring inner clamp, 3 is a first spring outer clamp, 4 is a first inclined ring spring, 5 is a first groove, 6 is a second spring outer clamp, 7 is a second inclined ring spring, 8 is a third groove, 9 is a first groove a, 10 is a fourth groove, 11 is a rotating shaft, and 12 is a second groove.
Detailed Description
The present invention will be described in detail with reference to the accompanying drawings and specific embodiments.
A supporting device comprises a radial bearing 1, an inner spring clamp 2 is sleeved outside the radial bearing 1, a first outer spring clamp 3 is sleeved outside the inner spring clamp 2, and a first inclined coil spring 4 is arranged between the inner spring clamp 2 and the first outer spring clamp 3. The spring inner clamp 2 and the first spring outer clamp 3 are fixed through pins.
As shown in fig. 2, a first groove 5 matched with the first inclined coil spring 4 is formed along the circumference of the outer surface of the spring inner clamp 2, and the inclined coil spring 4 is located in the first groove 5.
As shown in fig. 3, a first groove a9 is formed along the circumference of the outer surface of the inner spring clamp 2, a second groove 12 adapted to the first groove a9 is formed along the circumference of the inner surface of the outer spring clamp 3, and the first canted coil spring 4 is located in a cavity formed by the first groove a9 and the second groove 12. The first inclined coil spring 4 is installed between the spring inner clamp 2 and the first spring outer clamp 3 in interference compression.
As shown in fig. 4, a second spring outer clamp 6 is sleeved outside the first spring outer clamp 3, a second inclined coil spring 7 is arranged between the first spring outer clamp 3 and the second spring outer clamp 6, and the inclination angles of the first inclined coil spring 4 and the second inclined coil spring 7 are opposite. A third groove 8 is formed along the circumference of the outer surface of the first spring outer clamp 3, a fourth groove 10 matched with the third groove 8 is formed along the circumference of the inner surface of the second spring outer clamp 6, and the second inclined coil spring 7 is positioned in a cavity formed by the third groove 8 and the fourth groove 10. The second canted coil spring 7 is in interference compression between the first spring outer clamp 3 and the second spring outer clamp 6. The third groove 8 is symmetrical to the second groove 12, and the first groove a9 is symmetrical to the fourth groove 10.
The ring sleeve type structure is adopted for matching, the inclination angles of the first inclined ring spring 4 and the second inclined ring spring 7 are symmetrical (different), the first spring outer clamp 3 synchronously rotates along with the stress deformation of the first inclined ring spring 4 and the second inclined ring spring 7, and the circumferential force and the circumferential rotation of the inclined ring springs when the inclined ring springs are applied to the flexible supporting device can be compensated.
An anti-seismic device using a supporting device is shown in fig. 5, and comprises a rotating shaft 11, wherein the supporting device is sleeved on the rotating shaft 11.
The radial bearing 1 is located at the midpoint of the rotating shaft 11. The shaft 11 may be a slender rotating shaft, a drive train in a wind turbine tower or a workshop machining lathe shaft, or other rotating shaft, etc.
The rotating shaft 11 is a slender rotating shaft, and as shown in fig. 6 and 7, the oblique first inclined coil spring 4 with a fixed deflection angle is obtained by changing the deflection angle of the first inclined coil spring 4 in the winding process; deflection angle in the 4 coiling processes of first oblique coil spring equals with the cone angle of long and thin revolving axle conical surface department, and the impact force during the atress is parallel with the minor axis in 4 cross-sections of first oblique coil spring, can greatly improve first oblique coil spring 4's elastic property to strengthen the utility model discloses flexible strutting arrangement's shock-absorbing capacity and radial displacement's compensation ability.
As shown in fig. 8, the first inclined coil spring 4 with the special-shaped cross section suitable for different contact matching occasions is obtained by changing the shape of the spring cross section, and the slender revolving shaft anti-vibration device designed by the first inclined coil spring 4 with the special-shaped cross section can be used for the vibration absorption or vibration isolation of shaft structures under different contact matching requirements.
The supporting devices comprise a plurality of supporting devices, and each supporting device is uniformly distributed at a point generating large offset distance when the rotating shaft 11 rotates.
As shown in fig. 9, the supporting devices of the plurality of radial inclined coil springs are of a tandem structure and are uniformly distributed on the same slender rotating shaft, and the supporting devices of the tandem structure are uniformly distributed on the same slender shaft or are arranged at a position where a plurality of offset distances are larger when the slender shaft rotates automatically, so that the stability of the slender shaft can be improved; the larger allowable deformation of the inclined ring spring ensures that the serial connection type supporting structure still has good coaxiality; the required flexible support of the integral component rigidity can be obtained by connecting the inclined coil springs with different rigidities in series, so that different rigidity requirements are met.
The working principle of the utility model is as follows:
(1) the stress analysis of a single-circle inclined coil spring of the inclined coil spring under an ideal condition is firstly carried out, the problem can be considered as the stress analysis of a special simple support beam, as shown in figure 10, the inclination angle of the inclined coil spring is α, F is the force in any direction applied to a point B, F is equivalent to a force Fb1 of a vertical base plane and a force Fb2 of a parallel base plane, a force Fb2 of the parallel and base planes of ① can be considered as the resultant force of compression forces of the point B to a point A, C (namely the resultant force of the compression forces of the front half circle and the rear half circle of the single-circle spring respectively), the resultant force of the support reaction of a contact point A, C under the Fb2 is- Fb 2, and ② is used for the Fb1 to obtain the stress conditions of the points A and C by respectively taking moments of the point A and the point C.
By sigma MBWhen the result is 0:
FA+FC＝-Fcos(α)sin(α)
when the single-turn springs are superimposed at A, C points on the left and right, the ideal case is that the support reaction force at the unstressed turn contact point of the oblique-turn spring is-Fcos (α) sin (α), and the elastic force of the oblique-turn spring against the rigid body to which the load is applied is Fb1, as shown in fig. 11.
(2) The stress deformation condition of the whole circle of inclined coil spring can be superposed according to the stress deformation of a single coil spring, or analyzed by finite element software. The stressed deformation of the whole circle of spring after being loaded is as shown in figure 12, the deformation and the elasticity at the central point of the load are maximum, then the deformation is gradually reduced, the elasticity borne by each single circle is completely decomposed into radial component force and tangential component force, the radial component force and the tangential component force are respectively subjected to translational superposition, and the concentrated force F '(F' points to the circle center, and the direction is opposite to the offset direction) and the couple M (the rotating direction of the couple is the same as the elastic direction of the spring) opposite to the applied force F are obtained, so the spring has the centering characteristic. Although the radial inclined coil spring has good centering performance, the couple M of the radial inclined coil spring can enable the shaft to generate friction, the damping and centering of the inclined coil spring are influenced, and circumferential rotation can be avoided through reasonable structural design.
The annular structure leads the stress of the contact points to be distributed annularly, the center is symmetrical and the contact points are inclined to center, so the annular structure has good centering property.
The inclined coil spring deforms along with the radial deflection of the shaft, contact points of the inclined coil spring and the inner clamp and the outer clamp (the inner clamp and the outer clamp of the first inclined coil spring 4 are the spring inner clamp 2 and the first spring outer clamp 3) simultaneously displace when the inclined coil spring deforms, the deformation of a single-coil contact point is shown in fig. 13, and the radial displacement change when the inclined coil spring is loaded is related to the change coupling of the inclination angle α.
This results in the complete spring being displaced circumferentially toward the load center point and contracting, deforming as shown in fig. 13. The radial displacement of the loaded single coil of the inclined coil spring is along the circumferential direction from the load center point: the radial displacement of each single circle is gradually reduced, and the inclination angle of each single circle is also gradually reduced along the circumference to the elasticity FD of perpendicular to the base plane also reduces in proper order, and to the diameter GH department of perpendicular load direction, the impact force is zero, only the pretightning force. When the impact is too large, the pretightening force is completely released in the load negative direction, and even a gap is generated.
The utility model discloses a strutting arrangement's working process as follows:
when the supporting device of the utility model is acted by the radial force of the slender revolving shaft, the radial force is transmitted to the inner spring clamp 2 through the radial bearing 1 and then transmitted to the first inclined coil spring 4 through the inner spring clamp 2, because the outer spring clamp 3 is fixed, the first inclined coil spring 4 is deformed under pressure until the compressive deformation resistance of the first inclined coil spring 4 can balance the received radial force, the annular structure of the first inclined coil spring 4 enables the stress of the contact point of the first inclined coil spring 4 to be distributed annularly, symmetrical centrally and inclined to be centered, and the supporting device has good centering property; when the inner ring of the radial bearing 1 is driven to rotate, the steel ball of the radial bearing 1 can act on the outer ring of the radial bearing 1 to generate circumferential friction force, the circumferential friction force is transmitted to the first spring outer clamp 3 through the outer ring of the radial bearing 1, the circumferential friction force is transmitted to the first inclined ring spring 4 through the first spring outer clamp 3, and the circumferential friction force of the first inclined ring spring 4, the spring inner clamp 2 and the first spring outer clamp 3 offsets the circumferential displacement of the spring inner clamp 2.
When the ring sleeve type structure is adopted, the first spring outer clamp 3 synchronously rotates along with the stress deformation of the first inclined ring spring 4 and the second inclined ring spring 7, and the circumferential force and the circumferential rotation of the inclined ring springs when the inclined ring springs are applied to the flexible supporting device can be compensated.
Through the mode, the inclined ring spring with the annular structure between the spring inner clamp 2 and the first spring outer clamp 3 of the supporting device of the utility model can bear compression deformation, has good return performance, can still ensure normal work under impact, vibration and severe environment, and has simple structure; the utility model discloses an use strutting arrangement's antidetonation device, this above-mentioned strutting arrangement can effectively compensate long and thin revolving axle when long and thin revolving axle autogyration in the radial offset distance of arbitrary direction and other installation error etc..
Claims (10)
1. The utility model provides a support device, its characterized in that includes radial bearing (1), anchor clamps (2) in the spring have been cup jointed outward in radial bearing (1), anchor clamps (3) are outer to the outer anchor clamps (3) of first spring have been cup jointed in spring (2), be provided with first oblique circle spring (4) between anchor clamps (2) and the outer anchor clamps (3) of first spring in the spring.
2. The supporting device as claimed in claim 1, wherein a first groove (5) is formed along the circumference of the outer surface of the spring inner clamp (2), and the inclined coil spring (4) is located in the first groove (5).
3. The supporting device according to claim 1, wherein a first groove a (9) is formed along the circumference of the outer surface of the inner spring clamp (2), a second groove (12) matched with the first groove a (9) is formed along the circumference of the inner surface of the outer spring clamp (3), and the first inclined ring spring (4) is located in a cavity formed by the first groove a (9) and the second groove (12).
4. A supporting device as claimed in claim 3, characterized in that a second spring outer clamp (6) is sleeved outside the first spring outer clamp (3), a second canted coil spring (7) is arranged between the first spring outer clamp (3) and the second spring outer clamp (6), and the angles of inclination of the first canted coil spring (4) and the second canted coil spring (7) are opposite.
5. The supporting device according to claim 4, wherein a third groove (8) is formed along the circumference of the outer surface of the first spring outer clamp (3), a fourth groove (10) matched with the third groove (8) is formed along the circumference of the inner surface of the second spring outer clamp (6), and the second inclined ring spring (7) is positioned in a cavity formed by the third groove (8) and the fourth groove (10).
6. A supporting device as claimed in claim 5, characterised in that the third recess (8) is symmetrical to the second recess (12); the first groove a (9) and the fourth groove (10) are symmetrical.
7. An anti-seismic device using a supporting device, characterized by comprising a rotating shaft (11), wherein the supporting device according to any one of claims 1-6 is sleeved on the rotating shaft (11).
8. An anti-seismic device using supporting device according to claim 7, characterized in that said rotating shaft (11) is an elongated rotating shaft, said radial bearing (1) being located at the midpoint of the rotating shaft (11).
9. An anti-seismic device using supporting devices, according to claim 8, characterized in that said supporting devices comprise a plurality of supporting devices, each of which is uniformly distributed at the point where the rotating shaft (11) rotates with a large offset distance.
10. An anti-seismic device using supporting device according to claim 7, characterized in that the deflection angle of the first and second canted coil springs (4, 7) during winding is equal to the taper angle at the conical surface of the slender rotating shaft.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920613496.8U CN210371655U (en) | 2019-04-30 | 2019-04-30 | Supporting device and anti-seismic device applying same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920613496.8U CN210371655U (en) | 2019-04-30 | 2019-04-30 | Supporting device and anti-seismic device applying same |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN210371655U true CN210371655U (en) | 2020-04-21 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201920613496.8U Active CN210371655U (en) | 2019-04-30 | 2019-04-30 | Supporting device and anti-seismic device applying same |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN210371655U (en) |
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2019
- 2019-04-30 CN CN201920613496.8U patent/CN210371655U/en active Active
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| Date | Code | Title | Description |
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| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20220629 Address after: 710000 room 10903, block D, Zhongtian times, hanghang Second Road, National Aviation high tech industry base, Xi'an, Shaanxi Province Patentee after: Xi'an Xusheng Precision Manufacturing Co.,Ltd. Address before: 710048 Shaanxi province Xi'an Beilin District Jinhua Road No. 5 Patentee before: XI'AN University OF TECHNOLOGY |
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| TR01 | Transfer of patent right |