The DJM Type Single Flexible Diaphragm Coupling connects two shafts through a single stainless steel diaphragm pack bolted alternately to each hub flange. Covering 41 sizes from 9.8 N·m to 8,100,000 N·m at speeds up to 20,000 rpm, it is lubrication-free, torsionally rigid, and suited to high-speed pumps, compressors, turbines, and precision drives demanding zero backlash and minimal maintenance.
MOQ: 50 pcs. Minimum order value USD 1,500; mixed orders and trial quantities welcome.
DJM Type Single Flexible Diaphragm Coupling is presented here as an engineering selection page rather than a repetition of catalogue copy. The purpose is to make the operating logic, dimensional checks and ordering information easier to review while keeping the original technical values intact.
Torque is carried through thin metallic diaphragm elements that flex elastically to accommodate limited shaft displacement. Because the torque path is metallic and does not rely on sliding gear teeth or an elastomer spider, the coupling can provide high torsional stiffness, zero-backlash behavior and clean operation without routine lubrication.
Metal diaphragm elements transmit torque with limited rotational wind-up compared with elastomeric designs.
The flexible metallic element operates without grease lubrication at the flexing element.
Diaphragm flexure accommodates specified shaft displacement while maintaining a precise torque path.
Routine checks focus on fasteners, hubs, diaphragm condition and alignment rather than lubricant replacement.
The diaphragm pack should flex within its designed range rather than being used to correct large installation errors. Angular and axial displacement produce cyclic stress in the membranes, while shaft spacing and intermediate members influence lateral critical speed. High-speed applications therefore require attention to balance, runout and the complete rotor system, not only the nominal torque rating.
Establish the design torque from normal and transient loads, then verify the coupling speed, bore capacity, hub connection, axial allowance and angular compensation. Single- and double-flex arrangements are not interchangeable in every installation: double-flex configurations are generally chosen when direct parallel-offset accommodation is required, while single-flex versions are useful where the system geometry controls radial displacement.
Use the tables below as the dimensional and model reference. Confirm bore, shaft fit, speed, torque and installation envelope before final selection.
| Feature | DJM Diaphragm | Gear Coupling | Jaw / Spider | Grid Coupling |
|---|---|---|---|---|
| Lubrication | None ever | Grease essential | None | Grease required |
| Backlash | Zero | Low–medium | Low | Medium |
| Torsional stiffness | Very high | High | Low–medium | Medium |
| Max speed (standard) | 20,000 rpm | High | 15,300 rpm | Medium |
| Temperature range | -40°C to +280°C | -20°C to +120°C | -35°C to +80°C | -20°C to +100°C |
| Vibration damping | Low (stiff) | Low | High | Medium |
| Size | Nom. Torque N·m | Max Speed rpm | Bore d mm | D mm | A mm | B mm | L mm | J mm | Axial comp. mm | Angle comp. | Weight kg |
|---|---|---|---|---|---|---|---|---|---|---|---|
| 00 | 9,800 | 20,000 | 3–20 | 57 | 4.9 | 20 | 44.9 | 10 | ±0.8 | 1° | 0.4 |
| 01 | 33,000 | 20,000 | 5–22 | 68 | 6.1 | 26 | 58.1 | 13 | ±0.8 | 1° | 0.6 |
| 02 | 90,000 | 20,000 | 6–32 | 81 | 6.6 | 26 | 58.6 | 16 | ±1.0 | 1° | 1.1 |
| 03 | 173,000 | 18,000 | 8–35 | 93 | 8.4 | 29 | 66.4 | 22 | ±1.2 | 1° | 1.7 |
| 04 | 245,000 | 15,000 | 10–42 | 104 | 11.2 | 34 | 79.2 | 20 | ±1.4 | 1° | 2.5 |
| 05 | 420,000 | 13,000 | 15–50 | 126 | 11.7 | 42 | 95.7 | 25 | ±1.6 | 45' | 4.3 |
| 06 | 772,000 | 12,000 | 20–60 | 143 | 11.7 | 48 | 107.7 | 28 | ±1.8 | 45' | 6.9 |
| 07 | 1,270,000 | 10,000 | 25–75 | 168 | 16.8 | 58 | 132.8 | 23 | ±2.0 | 45' | 11.3 |
| 08 | 2,080,000 | 10,000 | 30–82 | 194 | 17.0 | 64 | 145 | 30 | ±2.2 | 45' | 16.7 |
| 09 | 3,328,000 | 9,000 | 30–95 | 214 | 21.6 | 77 | 175.6 | 22 | ±2.4 | 45' | 22.7 |
| 10 | 4,900,000 | 8,000 | 40–108 | 150 | 23.9 | 89 | 201.9 | 23 | ±2.6 | 45' | 35.4 |
| 11 | 6,368,000 | 8,000 | 52–118 | 276 | 27.2 | 102 | 231.2 | 40 | ±2.8 | 45' | 52.0 |
| 12 | 8,900,000 | 6,300 | 60–110 | 276 | 17.5 | 128 | 273.5 | – | ±1.8 | 45' | 57.2 |
| 13 | 15,280,000 | 5,000 | 60–135 | 308 | 19.0 | 160 | 339 | – | ±2.0 | 30' | 77.3 |
| 14 | 25,410,000 | 4,700 | 60–155 | 350 | 21.5 | 182 | 385.5 | – | ±2.0 | 30' | 123 |
| 15 | 37,130,000 | 4,300 | 60–165 | 375 | 24.0 | 198 | 420 | – | ±2.0 | 30' | 156 |
| 16 | 47,120,000 | 3,900 | 70–180 | 410 | 29.5 | 214 | 457.5 | – | ±2.2 | 30' | 191 |
| 17 | 57,000,000 | 3,500 | 70–190 | 445 | 29.5 | 225 | 479.5 | – | ±2.2 | 30' | 245 |
| 18 | 63,186,000 | 3,500 | 80–205 | 470 | 31.0 | 248 | 527 | – | ±2.4 | 30' | 329 |
| 19 | 82,590,000 | 3,200 | 90–230 | 512 | 32.0 | 278 | 588 | – | ±2.4 | 30' | 394 |
| 20 | 102,100,000 | 2,800 | 90–255 | 556 | 32.5 | 305 | 642.5 | – | ±2.5 | 30' | 530 |
| 21 | 126,070,000 | 2,450 | 100–265 | 588 | 34.0 | 318 | 670 | – | ±2.7 | 30' | 619 |
| 22 | 146,350,000 | 2,150 | 100–275 | 630 | 34.5 | 332 | 698.5 | – | ±2.8 | 30' | 683 |
| 23 | 173,830,000 | 2,000 | 100–290 | 655 | 35.5 | 348 | 731.5 | – | ±3.0 | 30' | 791 |
| 24 | 200,000,000 | 1,400 | 210–305 | 680 | 44 | 350 | 744 | – | ±3.5 | 30' | 980 |
| 25 | 250,000,000 | 1,250 | 225–340 | 745 | 44 | 350 | 744 | – | ±4.0 | 30' | 1100 |
| 26 | 315,000,000 | 1,200 | 250–365 | 785 | 50 | 350 | 750 | – | ±4.2 | 30' | 1300 |
| 27 | 400,000,000 | 1,150 | 270–380 | 830 | 50 | 380 | 810 | – | ±4.5 | 30' | 1500 |
| 28 | 500,000,000 | 1,100 | 290–400 | 875 | 50 | 400 | 850 | – | ±4.8 | 20' | 1700 |
| 29 | 630,000,000 | 1,000 | 320–425 | 935 | 60 | 400 | 860 | – | ±5 | 20' | 2100 |
| 30 | 800,000,000 | 930 | 340–440 | 1030 | 60 | 440 | 940 | – | ±5.2 | 20' | 2600 |
| 31 | 1,000,000,000 | 880 | 380–460 | 1080 | 66 | 460 | 986 | – | ±5.5 | 20' | 2900 |
| 32 | 1,250,000,000 | 820 | 400–500 | 1160 | 70 | 520 | 1110 | – | ±5.8 | 20' | 3500 |
| 33 | 1,600,000,000 | 740 | 420–560 | 1290 | 82 | 570 | 1222 | – | ±6.2 | 20' | 5100 |
| 34 | 2,000,000,000 | 680 | 440–600 | 1410 | 92 | 570 | 1232 | – | ±6.5 | 20' | 5900 |
| 35 | 2,500,000,000 | 620 | 450–650 | 1530 | 105 | 610 | 1325 | – | ±6.8 | 20' | 6800 |
| 36 | 3,020,000,000 | 570 | 500–710 | 1670 | 115 | 730 | 1575 | – | ±7.2 | 20' | 7900 |
| 37 | 4,050,000,000 | 520 | 600–780 | 1830 | 125 | 800 | 1725 | – | ±7.5 | 20' | 10700 |
| 38 | 5,300,000,000 | 480 | 650–860 | 2000 | 130 | 800 | 1730 | – | ±7.8 | 20' | 14000 |
| 39 | 6,600,000,000 | 430 | 700–945 | 2200 | 140 | 960 | 2060 | – | ±8.0 | 20' | 17100 |
| 40 | 8,100,000,000 | 400 | 800–1030 | 2400 | 140 | 960 | 2060 | – | ±8.2 | 20' | 21100 |
| Load Character | K | Typical Applications |
|---|---|---|
| Electric motor, smooth / uniform | 1.25–1.50 | Centrifugal pumps, fans, generators |
| Electric motor, moderate shock | 1.50–2.00 | Compressors, mixers, reciprocating pumps |
| IC engine, 4-cylinder+, moderate shock | 2.00–2.50 | Diesel pump sets, marine auxiliaries |
| Heavy shock / frequent reversal | 2.50–3.00 | Crushers, hoists, rolling mill drives |
| Criterion | DJM (Single) | SJM (Double) |
|---|---|---|
| Axial compensation | ±0.8–±8.2 mm | ±1.6–±16.4 mm |
| Angular compensation | Up to 1° | Up to 2° |
| Radial compensation | Via angular flex only | Direct radial: 0.5–3.0 mm |
| Overall length | Shorter | Longer |
| Best for | Well-aligned, space-limited drives | Multi-axis misalignment; long shaft spans |
| Symptom | Likely Cause | Action |
|---|---|---|
| Excessive vibration | Shaft misalignment beyond limits; diaphragm fatigue | Re-align shafts; inspect diaphragm pack for cracks |
| Diaphragm cracking | Chronic overload; misalignment exceeding limits; incorrect bolt torque | Replace diaphragm pack; recalculate TC; verify alignment |
| Bolt hole fretting / wear marks | Under-torqued bolts allowing micro-slip | Replace diaphragm; retorque all bolts to spec |
| Hub bore fretting | Inadequate interference fit; loose setscrew | Verify fit tolerance; re-torque setscrews |
Keep flange faces, pilot surfaces and diaphragm packs clean. Align shafts before tightening the membrane fasteners and use the specified tightening sequence so clamp load is distributed evenly. Avoid bending, scratching or prying against the thin flexible elements. On spacer or intermediate-shaft versions, verify the assembled distance between shaft ends and check rotor balance for the intended operating speed.
Measure the actual shaft diameters and keyways before machining or confirming a finished bore. A drawing should identify shaft tolerances, key dimensions, required hub position and any shoulder, locknut or axial-retention feature. Alignment readings should be taken after the machine is in its normal installed condition because base distortion, pipe strain, belt pull or thermal growth can move the shaft centers after an initial bench alignment.
After assembly, turn the drive through at least one full revolution by hand where practical. Check for interference with guards, brake hardware and adjacent structures, then verify fastener security. On equipment that changes temperature significantly between start-up and steady operation, compare cold and hot alignment expectations before setting final offsets.
No grease change is required, but visual and vibration monitoring remain important. Inspect for diaphragm cracking, fretting around bolt holes, loose fasteners, corrosion and unusual shaft movement. If a pack is replaced, investigate the root cause—commonly overload, excessive misalignment, incorrect bolt preload or an operating condition near a lateral critical speed.
A coupling should not be used as a permanent correction for poor machine alignment. If vibration, temperature or noise changes after commissioning, compare the current condition with the initial baseline. Check connected bearings and shafts at the same time, because many coupling symptoms originate from looseness, soft foot, imbalance or movement elsewhere in the drivetrain.
For planned maintenance, record the installed model, actual bore sizes, fastener details, lubricant or flexible-element grade where applicable, and the measured alignment at return to service. That information makes later inspection more useful and helps distinguish normal wear from a change in machine condition.
No. Motor power is only a starting point. The selection should use actual torque, service factor, peak load, speed and the driven-machine characteristics.
Confirm the shaft interface first, then the overall installation envelope. Bore, key or locking method, hub length, pilot or flange details and available removal clearance all affect whether a listed model will fit.
Use the model-specific limit as a maximum capability, not as the target installation condition. Better initial alignment usually reduces cyclic load, heat and wear in both the coupling and connected bearings.
Provide a dimensioned shaft drawing or at minimum the shaft diameter and tolerance, keyway, engagement length, shoulder or axial-retention details and required hub position.
Yes. A short follow-up inspection after the machine has run under real load can reveal fastener settlement, lubricant leakage, unexpected movement or alignment change before these develop into a larger problem.
Treat the listed values as the model reference. Select a candidate from torque and speed, then verify every geometric field that affects your installation before issuing the final order drawing.
Used where torsional stiffness and controlled alignment are important to drivetrain behavior.
Applicable to rotating machinery where clean, lubrication-free coupling elements are preferred.
Considered when balance, speed, shaft fit and alignment are verified for the selected configuration.
Suitable for engineered drivetrains that require repeatable torque transmission and documented installation geometry.
Typical duties include pumps, compressors, turbines, test equipment, high-speed machinery, precision industrial drives and long-span shaft connections. The correct configuration depends on torque, speed, misalignment mode, shaft spacing and balance requirements.
The same coupling family can behave very differently in a smooth continuous drive and in a reversing, impact-loaded or frequently started drive. For that reason, application name alone is not enough for selection. Supply the operating torque, peak load, speed, shaft dimensions, expected movement, ambient conditions and required service access so the configuration can be checked against the complete duty.
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