CN101871497A - Rigid spring - Google Patents
Rigid spring Download PDFInfo
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- CN101871497A CN101871497A CN 201010214905 CN201010214905A CN101871497A CN 101871497 A CN101871497 A CN 101871497A CN 201010214905 CN201010214905 CN 201010214905 CN 201010214905 A CN201010214905 A CN 201010214905A CN 101871497 A CN101871497 A CN 101871497A
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Abstract
The invention discloses a rigid spring, which is in a hollow cylinder structure. The cylinder is coaxially provided with at least one concave diameter changing part which is a groove on the longitudinal section of the spring, the proportion of the depth of the groove to the width of the spring cylinder is 1-4:10, and the included angle alpha formed by two start parts of the groove and the bottom of the groove is 45-150 degrees. The invention develops a novel spring, which has high rigidity, can replace a washer for use, and can be applied to fill the gap of a device with larger load.
Description
Technical field
The present invention relates to a kind of spring, be specifically related to a kind of stiffness spring.
Background technique
Spring is a kind of mechanical parts that utilize elasticity to come work, has obtained at present using very widely.According to the spring shape, can be divided into belleville spring, annular spring, leaf spring, helical spring, valute spring and torsion bar spring etc., in general its manufactured materials should have high limit of elasticity, fatigue limit, impact toughness and good heat treatment performance etc., and commonly used have carbon spring steel, alloy spring steel, rustproof spring steel and Cuprum alloy, nickel alloy and a rubber etc.
On the other hand, in mechanical industry, often some filling components need be installed in equipment,, prevent that both from directly colliding with, and plays the effect of buffering to fill two gaps between the parts.Because equipment can produce strenuous vibration in operation, rock or situation such as working conditions change, little when big when causing gap between the two, therefore require above-mentioned filling component to have fabulous rigidity, and has certain elasticity, make filling component fill up also all the time tensioner plays the effect of automatic compensation in the gap.At present, maximum filling component of usefulness is a helical spring, yet its rigidity is generally less, and when being subjected to big load, spring may plastic deformation and lost efficacy; And if select pad or packing ring for use, when working conditions change causes the gap to become big, can't play the effect of automatic compensation again.
Summary of the invention
The object of the invention provides a kind of stiffness spring with high rigidity.
For achieving the above object, the technical solution used in the present invention is: a kind of stiffness spring, described spring is the hollow cylinder structure, the coaxial reducing portion that is provided with at least one indent on the cylinder, described reducing portion is groove on the spring longitudinal section, the ratio of the degree of depth of groove and spring cylinder width is 1～4: 10, and the angle a that forms between 3 of two initial part of groove and the bottom portion of groove is 45～150 degree.
Above, described spring is the hollow cylinder structure, and it can be cylinder, cylindroid or square column, preferred cylinder.Reducing portion on the described cylinder can be one or more, and when being provided with 2 above reducing portions, the size of these reducing portions and the degree of depth can be identical or different; Described reducing portion is groove on the spring longitudinal section, and this groove can be circular arc, parabola, V-arrangement or U-shaped etc.
Experiment finds, when the depth of groove and the cylinder width ratio of reducing portion exceeds 40%, then rigidity descends a lot; And ratio is less than 10% o'clock, and then rigidity is too high again, and amount of deformation is too little, the elasticity deficiency.The scope of described angle a as less than 45 degree, then be unfavorable for processing, and stress is concentrated easily; And angle is excessive, surpasses 150 degree, and then rigidity is too high, and amount of deformation is too little, the elasticity deficiency.
Optimized technical scheme, described spring is the hollow cylinder body structure, cylinder is provided with 1 reducing portion, described reducing portion is arc groove on the spring longitudinal section, the ratio of the degree of depth of groove and spring column diameter is 1: 7, and the angle a that forms between 3 of two initial part of groove and the bottom portion of groove is 90 degree.
Optimized technical scheme, described spring is the hollow cylinder body structure, cylinder is provided with 2 identical reducing portions, described reducing portion is v-depression on the spring longitudinal section, the ratio of the degree of depth of groove and spring column diameter is 4: 10, and the angle a that forms between 3 of two initial part of groove and the bottom portion of groove is 45 degree.
Stiffness spring of the present invention has very high rigidity, has certain compressible amount again, and its rigidity can also be as requested, waits by structure, size, the quantity that changes reducing portion and realizes.The internal stress of stiffness spring of the present invention under in working order is very low, and distribution uniform can be born big load by small scale structures.Can apply precompressed (or prestretching) earlier in use, store certain energy in spring, when thrust load became big, spring can be continued trace compression (or stretching), and when working conditions change produced the gap, this spring can automatic small compensation.In addition, in order to reduce the contact stress of both ends of the spring face, with two ends do big slightly; Problem such as concentrate for fear of stress, all transition wires all are circular curve, and radius of arc all has strict demand.The groove of spring, purpose provides resiliently deformable, realizes compensation automatically.Discover that the rigidity of this spring is mainly by this cylindrical shell thickness, groove structure and the decision of groove quantity.Simultaneously, the equivalent stress distribution of spring is also relevant with simplified thickness, groove shapes, each transition position chamfering, when design, should take into account values of stiffness and equivalent stress simultaneously, and is indispensable.
Because the employing of technique scheme, compared with prior art, the present invention has following advantage:
1. the present invention has developed a kind of new spring, and it has high rigidity, and rigidity can reach 20000N/0.01mm, compares with the helical spring of same specification, and the rigidity of spring of the present invention is helical spring more than 20 times, has significant effect.
2. spring of the present invention not only has high rigidity, has certain compressible amount again, alternative packing ring uses, can be applicable to fill in the equipment gap with big load, can apply precompressed (or prestretching) earlier during use, in spring, store certain energy, when thrust load becomes big, spring can be continued trace compression (or stretching), and when working conditions change produced the gap, this spring can automatic small compensation.
3. spring structure of the present invention is simple, be easy to preparation, and cost is lower, is suitable for industrial applications.
Description of drawings
Accompanying drawing 2 is longitudinal sections of the embodiment of the invention two;
Accompanying drawing 3 is application schematic representation of the embodiment of the invention one.
Wherein: 1, groove; 2, leading screw; 3, flange; 4, locking nut; 5, screw; 6, bearing; 7, oil sealing; 8, bearing inner spacing collar; 9, inner spacing collar; 11, stiffness spring; 12, supporting base.
Embodiment
Below in conjunction with drawings and Examples the present invention is further described:
Embodiment one:
Referring to shown in Figure 1, a kind of stiffness spring, described spring is the hollow cylinder body structure, cylinder is provided with 1 reducing portion, described reducing portion is v-depression 1 on the spring longitudinal section, the ratio of the degree of depth s of groove and spring column diameter r is 1: 7, and the angle a that forms between 3 of two initial part of groove and the bottom portion of groove is 90 degree.The axial length of above-mentioned spring is 20mm, and rigidity is 15000N/0.01mm.
Above-mentioned stiffness spring can be used for leading screw bearing pre-pressing structure, referring to shown in Figure 3, earlier inner spacing collar 9, oil sealing 7 are loaded on the leading screw 2 during assembling, again with integral installation on supporting base 12, bearing 6, stiffness spring 11, bearing inner spacing collar 8, inner spacing collar 9, oil sealing 7 are installed on the leading screw one by one, tight with locking nut 4 bands again, with screw 5 flange 3 is installed on the supporting base then, and flange 3 is fixed with the screw-down torque of torque spanner according to screw, calculate the amount of deformation of required spring, thereby learn the screw-down torque of locking nut, the integral body adjustment is installed and fixed.Its working principle is: in advance stiffness spring, bearing are carried out precompressed, when ambient temperature raise, because the leading screw material is different with the body material thermal expansion coefficient, leading screw can extend with respect to matrix, can come the absorption portion amount of deformation this moment by stiffness spring, thereby guarantee the suitable pretightening force of bearing; When ambient temperature reduces, when leading screw shortens with respect to matrix, also can come the absorption portion amount of deformation, thereby guarantee the suitable pretightening force of bearing by stiffness spring.In like manner, when the leading screw rotation causes leading screw self to heat up elongation, also can guarantee the suitable pretightening force of bearing.
Stiffness spring of the present invention can be adjusted the pretightening force of leading screw bearing automatically in certain scope, and bearing pre-fastening can be adjusted to the optimum state, avoid bearing assembling tension to influence the life-span, or bearing is crossed pine generation axial float, constantly keep transmission shaft to have suitable rigidity and elasticity, well improve the life-span of bearing, helped improving the precision stability of secret lathe.Simultaneously, can simplify assembly technology, raise the efficiency.
Embodiment two:
Referring to shown in Figure 2, a kind of stiffness spring, described spring is the hollow cylinder body structure, cylinder is provided with 2 identical reducing portions, described reducing portion is v-depression 1 on the spring longitudinal section, the ratio of the degree of depth s of groove and spring column diameter r is 4: 10, and the angle a that forms between 3 of two initial part of groove and the bottom portion of groove is 90 degree.The axial length of above-mentioned spring is 40mm, and rigidity is 12000N/0.01mm.
Embodiment three:
A kind of stiffness spring, described spring is the hollow cylinder body structure, cylinder is provided with 1 reducing portion, described reducing portion is arc groove on the spring longitudinal section, the ratio of the degree of depth of groove and spring column diameter is 1: 7, and the angle that forms between 3 of two initial part of groove and the bottom portion of groove is 90 degree.The wall thickness of above-mentioned spring is 3mm, and axial length is 20mm, and rigidity is 20000N/0.01mm.
Embodiment four:
A kind of stiffness spring, described spring is the hollow cylinder body structure, cylinder is provided with 2 different reducing portions, described 2 reducing portions are respectively v-depression and arc groove on the spring longitudinal section, the ratio of the degree of depth of v-depression and spring column diameter is 1: 10, the angle that forms between 3 of two initial part and the bottom portion of groove is 45 degree, and the ratio of the degree of depth of arc groove and spring column diameter is 4: 10, and the angle that forms between 3 of two initial part and the bottom portion of groove is 150 degree.
Claims (3)
1. stiffness spring, it is characterized in that: described spring is the hollow cylinder structure, the coaxial reducing portion that is provided with at least one indent on the cylinder, described reducing portion is groove (1) on the spring longitudinal section, the ratio of the degree of depth of groove and spring cylinder width is 1～4: 10, and the angle a that forms between 3 of two initial part of groove and the bottom portion of groove is 45～150 degree.
2. stiffness spring according to claim 1, it is characterized in that: described spring is the hollow cylinder body structure, cylinder is provided with 1 reducing portion, described reducing portion is v-depression on the spring longitudinal section, the ratio of the degree of depth of groove and spring column diameter is 1: 7, and the angle a that forms between 3 of two initial part of groove and the bottom portion of groove is 90 degree.
3. stiffness spring according to claim 1, it is characterized in that: described spring is the hollow cylinder body structure, cylinder is provided with 2 identical reducing portions, described reducing portion is v-depression on the spring longitudinal section, the ratio of the degree of depth of groove and spring column diameter is 4: 10, and the angle a that forms between 3 of two initial part of groove and the bottom portion of groove is 90 degree.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201010214905 CN101871497A (en) | 2010-07-01 | 2010-07-01 | Rigid spring |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201010214905 CN101871497A (en) | 2010-07-01 | 2010-07-01 | Rigid spring |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101871497A true CN101871497A (en) | 2010-10-27 |
Family
ID=42996539
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201010214905 Pending CN101871497A (en) | 2010-07-01 | 2010-07-01 | Rigid spring |
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| Country | Link |
|---|---|
| CN (1) | CN101871497A (en) |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3774896A (en) * | 1972-02-16 | 1973-11-27 | Temper Corp | Dual rate cylindrical spring |
| US3815887A (en) * | 1972-03-21 | 1974-06-11 | Hercules Inc | Plastic spring |
| US3970294A (en) * | 1973-08-21 | 1976-07-20 | Nissan Motor Co., Ltd. | Synchronous ring in a synchronous device |
| US7195235B2 (en) * | 2002-01-22 | 2007-03-27 | Rode John E | Adjustable disc spring systems and methods |
| CN101014782A (en) * | 2004-08-23 | 2007-08-08 | 默顿斯公司 | Compression spring and method for the production thereof |
-
2010
- 2010-07-01 CN CN 201010214905 patent/CN101871497A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3774896A (en) * | 1972-02-16 | 1973-11-27 | Temper Corp | Dual rate cylindrical spring |
| US3815887A (en) * | 1972-03-21 | 1974-06-11 | Hercules Inc | Plastic spring |
| US3970294A (en) * | 1973-08-21 | 1976-07-20 | Nissan Motor Co., Ltd. | Synchronous ring in a synchronous device |
| US7195235B2 (en) * | 2002-01-22 | 2007-03-27 | Rode John E | Adjustable disc spring systems and methods |
| CN101014782A (en) * | 2004-08-23 | 2007-08-08 | 默顿斯公司 | Compression spring and method for the production thereof |
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| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C02 | Deemed withdrawal of patent application after publication (patent law 2001) | ||
| WD01 | Invention patent application deemed withdrawn after publication |
Open date: 20101027 |