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Disc Springs DIN 2093
A brief history - The humble Disc Spring Washer was introduced to the world by Julien-Francoise Belleville and patented as early as 1861. This early form of Disc Spring in the form of an annular type shell was able to absorb very high axial forces with very small amounts of deflection.
Over the years the Disc Spring has become more finely honed with greater degrees and accuracy for both forces and deflections.
With the introduction of DIN 2092 calculations, it is now possible to either select or design a Disc to meet a customers specific requirement.
Caleb Components can offer a large choice of standard Discs Springs or even design and provide a special to suit your requirements. With our specialist Disc Data program we can provide a print-out covering all the relevant details. |
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Some common uses for
Disc Springs
- Stiffeners for hinges
- Spring return on press tooling
- Excellent shock absorption
- Clutch return Spring pressure
- Helps prevent bolt loosening
- Clearance take-up
- Provides pressure between cutting blades
- Pre-loading of Ball-Bearing units
- Stacked to form a spring stack
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Some advantages of
Disc Springs
- High force for short movements
- Even loading throughout circumference
- Various Spring characteristics:
- Linear, regressive and negative rates
- Numerous combinations
- Non-tangle (for automated assembly)
- High shock absorption
- High number of cycles achievable
- Replacement for coil springs
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General operating temperatures:
0.2 to under 1.25mm thickness (Carbon Spring Steel) -10 to +100 Degrees
1.25mm thickness and above (50 CrV4 Chrome Vanadium -40 to + 200 Degrees
Caleb Components can generally offer high volume customer specials in as little as 4 ~ 6 weeks with either minimal or no tooling costs involved and to the highest degree of quality for maximum fatigue life. |
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Stacked in Parallel
Deflection: As a single Disc.
Force: As per single Disc multiplied by the number of Discs in parallel. |
Stacked in series
Deflection: As per single Disc multiplied by number of Discs in series.
Force: As a single Disc. |
Stacked in series & parallel
Deflection: As per single Disc multiplied by number of Discs in series.
Force: As per single Disc multiplied by the number of Discs in parallel. |
Note! Hysteresis increases the load by approximately 3% per mating face per Disc. Eg if 3 Discs are in parallel the load would increase by approximately 6% (2 mating faces x 3%). |
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Recommended O/Dia & I/Dia clearances
| Diameter |
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Diameter Clearance |
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| up to 16mm |
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0.2mm |
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| Over 16.0mm to 20.0mm |
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0.3mm |
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| Over 20.0mm to 26.0mm |
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0.4mm |
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| Over 26.0mm to 31.5mm |
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0.5mm |
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| Over 31.5mm to 59.0mm |
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0.6mm |
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| Over 59.0mm to 80.0mm |
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0.8mm |
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| Over 80.0mm to 140.0mm |
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1.0mm |
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| Over 140mm to 250.0mm |
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1.6mm |
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To minimise friction and obtain a more accurate force the correct guiding element and clearance should be used. (see enclosed table)
Although it is common to guide Disc Springs on a shaft it is acceptable for them to be guided via the outside dia in an enclosed bore.
To prevent excessive wear on the guide element a minimum surface hardness of 55 HRC should apply to both guide and end abutments. |
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DIN 2093 Standard Disc Springs
F = Force in Newtons at 75% deflection |
Material:
Group 1 (< 1.25mm thk ):-
Carbon Spring Steel
Groups 2 & 3 (1.25mm thk plus ):-
50 CrV4 Chrome Vanadium Spring Steel
Stainless Steel available upon request.
Standard Finish:
Phosphate and oil |
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| Part no |
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De |
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Di |
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t |
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lo |
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ho |
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F at 75% |
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| To view the data tables and diagrams on this page in a black and white printable format, please visit our Online Catalogue page. |
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