Quick adjustable torque limiting safety coupling

Abstract

This invention relates to the field of coupling technology, and more particularly to a quick-adjustable torque-limiting safety coupling. Its technical solution includes a first half-coupling, a second half-coupling, a pin module, a transition flange, and an intermediate section. The first half-coupling has a transition flange on one side, and an intermediate section is located on one side of the transition flange. A pin module is located inside one side of the first half-coupling, and a large ball bearing is located inside the transition flange. The pin module includes a housing, a disc spring located on the side of the housing, a lower ball bearing located on the side of the disc spring, and a column located inside the housing. A signal trigger is located on one side of the first half-coupling. This invention achieves precise torque adjustment and instantaneous disengagement under overload by using a ring-shaped, evenly distributed pin module, symmetrical disc springs, and an inclined force transmission structure. Relying on a diaphragm assembly, an insulating plate, and a signal trigger, it achieves installation deviation compensation, electrical isolation, and overload signal feedback, combining mechanical and electrical safety, and is suitable for high-requirement continuous production conditions.

Description

Technical Field

[0001] This invention relates to the field of coupling technology, and more particularly to a quick-adjustable torque-limiting safety coupling. Background Technology

[0002] In industrial transmission systems, couplings are the core components connecting the drive end and the load end. Their safety protection performance directly determines the operational stability of the equipment and the service life of the core components. In traditional transmission systems, hydraulic, friction, and break-type safety couplings are commonly used overload protection devices, but they have many technical problems in practical applications.

[0003] Hydraulic safety couplings rely on hydraulic oil to transmit torque, which is significantly affected by fluctuations in ambient temperature and pressure. They have low torque control accuracy, and hydraulic oil is prone to leakage, causing environmental pollution. Maintenance requires specialized tools and spare parts, increasing operating costs. Friction couplings transmit torque through friction plates, but after long-term use, the friction plates wear out severely, leading to torque attenuation and requiring frequent replacement of parts, which cannot meet the needs of continuous production. Fracture couplings achieve overload protection by breaking components, but they are disposable products. After failure, the core components need to be disassembled and replaced, which takes a long time to reset and seriously affects production efficiency.

[0004] Meanwhile, with the improvement of industrial automation, the demand for overload protection response speed, signal feedback capability, and multi-dimensional safety protection of equipment is increasing. Traditional safety couplings generally have problems such as slow response, large residual torque, and lack of electrical insulation function. They are difficult to adapt to the harsh working conditions of industries such as chemical, power, and metallurgy with high requirements for electrostatic protection and explosion protection. Moreover, they cannot be linked with the automatic control system and cannot achieve integrated control of overload alarm and emergency shutdown. This can easily lead to the expansion of overload faults, causing damage to core components and significant economic losses. Therefore, those skilled in the art have provided a fast adjustable torque limiting safety coupling to solve the problems mentioned in the background art. Summary of the Invention

[0005] The purpose of this invention is to address the problems existing in the background art by proposing a fast-adjustable torque-limiting safety coupling.

[0006] To achieve the above objectives, the present invention provides the following technical solution: a quick-adjustable torque-limiting safety coupling, comprising a first half-coupling, a second half-coupling, a pin module, a transition flange, and an intermediate section. The first half-coupling has a transition flange on one side, an intermediate section on one side of the transition flange, and the second half-coupling on one side of the intermediate section. A pin module arranged in a ring-shaped column arrangement is disposed inside one side of the first half-coupling. Large pin balls arranged in a ring-shaped array are disposed inside the pin module corresponding to the transition flange. The pin module includes a housing, disc springs symmetrically distributed on the side of the housing, a lower pin ball on one side of the disc spring, and a column located inside the housing and at one end of the large pin ball, fitting against a small pin ball. A signal trigger is disposed on one side of the first half-coupling and on the side of the pin module.

[0007] Preferably, a connecting flange is provided between the intermediate section and the second half coupling. The connecting flange and the inner side of the intermediate section are provided with mounting holes arranged in a ring array. A drive bolt is installed inside the mounting hole, and a drive nut is threaded onto the outer wall of one end of the drive bolt.

[0008] Preferably, an insulating plate is provided between the connecting flange and the second half-coupling. The second half-coupling and the second connecting flange are both provided with mounting holes arranged in a ring array. A connecting bolt is screwed into the second mounting hole.

[0009] Preferably, a bearing is provided between the coupling and the transition flange. The bearing is arranged in two sets with a relatively distributed layout, and the inner wall raceway is inclined. Columnar rollers are rotatably installed inside the inclined raceway.

[0010] Preferably, the inner side of the intermediate section where it fits with the transition flange is provided with mounting holes three arranged in a ring array, and connecting bolts two are provided inside the mounting holes three.

[0011] Preferably, a diaphragm assembly is provided between the intermediate section and the transition flange. The diaphragm assembly is annular and has corresponding mounting holes and slots for connecting bolts to be assembled inside its sides.

[0012] Preferably, the inner wall of the transition flange and the outer wall of one end of the half coupling are both provided with annular grooves for bearing assembly, and a positioning ring located inside the transition flange and in contact with the inner ring of the bearing is provided on one side of the half coupling.

[0013] Preferably, both the positioning ring and the half coupling have mounting holes arranged in a ring array, and bolts are screwed into the mounting holes.

[0014] Preferably, the inner wall of the outer shell is provided with symmetrically distributed sliding grooves for assembling the disc spring, and one end of the disc spring is provided with a pressing block that fits against the small top bead. The side of the pressing block that fits against the small top bead is inclined, and the side of the small top bead that fits against the outer wall of the bead is inclined.

[0015] Preferably, the opening of the outer shell is provided with an end cap that is slidably assembled with the column. Both the end cap and the interior of the outer shell are provided with five mounting holes arranged in a ring array. Four bolts are screwed into the internal threads of the five mounting holes.

[0016] Compared with the prior art, the beneficial effects of the present invention are as follows:

[0017] In this invention, the half-coupling and the transition flange are connected by bearing assembly and locked and positioned by the ejector module unit. When the torque reaches the preset threshold, the ejector module overcomes the spring force of the disc spring and disengages from the slot, completing the disengagement action. The diaphragm group can effectively absorb the installation coaxiality deviation and the impact and vibration during operation. The insulating plate realizes the electrical insulation between the left and right half-couplings. The signal trigger monitors the displacement status of the ejector module in real time and outputs the switch signal. All components are arranged coaxially and the whole is cylindrical in structure, which greatly improves the convenience of installation and the alignment accuracy.

[0018] The device integrates a signal triggering mechanism. When the pin module is disengaged, it outputs a 24V DC signal synchronously, which can be directly used for equipment alarm or automatic shutdown interlock control. After reset, it can be quickly reset and put into operation without disassembling the whole machine. Its structure is simple and compact, and its response is accurate and efficient. It can adapt to the high reliability operation requirements under frequent overload conditions. It achieves mechanical transmission safety through torque limiting and electrical safety protection through electrical insulation structure.

[0019] With this safety coupling, the transmission chain can be quickly cut off when the equipment encounters overload, effectively avoiding the risk of damage to core components. The action signal feedback function helps to implement automated interlocking control, significantly improving the safety and stability of the whole machine operation. The overall structure is simple and compact, easy to install and operate, and requires no additional adjustment or maintenance for long-term operation, greatly reducing equipment downtime and maintenance costs. It is especially suitable for working conditions with high continuous production requirements and strict equipment protection standards. Attached Figure Description

[0020] Figure 1 This is the main sectional view of the present invention;

[0021] Figure 2 This is a main sectional view of the ejector pin module of the present invention;

[0022] Figure 3 This is a schematic diagram of the main cross-sectional three-dimensional structure of the present invention;

[0023] Figure 4 For the present invention Figure 3Schematic diagram of the three-dimensional structure of the middle section from the side;

[0024] Figure 5 For the present invention Figure 3 Schematic diagram of the three-dimensional structure of the intermediate transition flange;

[0025] Figure 6 For the present invention Figure 3 Schematic diagram of the three-dimensional structure of the bearing;

[0026] Figure 7 For the present invention Figure 3 A three-dimensional structural diagram of the middle half coupling from one side.

[0027] Reference numerals in the attached diagram: 1. Half-coupling one; 2. Half-coupling two; 3. Pin module; 4. Bearing; 5. Transition flange; 6. Diaphragm assembly; 7. Intermediate section; 8. Drive bolt; 9. Insulating plate; 10. Signal trigger; 11. Housing; 12. Disc spring; 13. Small pin; 14. Large pin; 15. Column; 16. End cap. Detailed Implementation

[0028] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0029] Please see Figures 1 to 7 The present invention provides three embodiments:

[0030] Example 1:

[0031] A quick-adjustable torque-limiting safety coupling includes a first half-coupling 1, a second half-coupling 2, a pin module 3, a transition flange 5, and an intermediate section 7. The transition flange 5 is located on one side of the first half-coupling 1, and the intermediate section 7 is located on one side of the transition flange 5. The second half-coupling 2 is located on one side of the intermediate section 7. The pin module 3, arranged in a ring-shaped column arrangement, is located inside the side of the first half-coupling 1. The transition flange 5, corresponding to the pin module 3, has large pin balls 14 arranged in a ring-shaped array inside. The pin module 3 includes a housing 11, disc springs 12 symmetrically distributed on the side of the housing 11, a lower pin ball located on one side of the disc springs 12, and a column 15 located inside the housing 11 and at one end of the large pin ball 14, which is in contact with a small pin ball 13. A signal trigger 10 is located on one side of the first half-coupling 1 and on one side of the pin module 3.

[0032] In this embodiment, half-coupling 1 and half-coupling 2 serve as the active end and passive end, respectively, and are connected to the drive shaft and load shaft through keyways. The surfaces are hardened to improve wear resistance. The transition flange 5 and the intermediate section 7 are the core transmission connection components. The transition flange 5 is forged from 45# steel, and two annular grooves are opened on the inner wall for assembling the bearing 4 assembly. The intermediate section 7 is forged from aluminum alloy and then anodized, which reduces the weight compared to traditional steel components while ensuring structural strength.

[0033] Multiple sets of ejector pin modules 3 are arranged in a ring array and evenly distributed on the end face of the half coupling 1 to form a omnidirectional uniform locking structure, ensuring force balance under overload. Each set of ejector pin modules 3 includes a housing 11, a disc spring 12, a pressing block, a small ejector ball 13, a column 15 and an end cap 16. The housing 11 is a stepped cylindrical structure made of alloy tool steel and heat-treated. Two sliding grooves are symmetrically opened on the inner wall for guiding and limiting the disc spring 12.

[0034] The disc spring 12 is a standard series stainless steel disc spring 12. Each set of ejector pin modules 3 has two symmetrically arranged disc springs 12. The pre-compression amount is adjusted to provide a stable clamping force and ensure the stability of the torque setting. The extrusion block has a wedge structure. The side that fits with the small ejector ball 13 is machined with a bevel. The surface of the small ejector ball 13 is ultra-precision machined to form point-to-surface contact with the bevel of the extrusion block and the end face of the column 15 to reduce frictional resistance. The column 15 has a stepped shaft structure. The end face fits with the large ejector ball 14 in the transition flange 5. The rear end slides with the end cover 16, and the sliding clearance is controlled to be small.

[0035] The end cover 16 is fixed to the outer shell 11 by multiple hexagonal bolts. The outer side of the end cover 16 integrates a dial. By rotating the end cover 16, the pre-compression of the disc spring 12 can be adjusted to achieve stepless adjustment of the disengagement torque. The dial range is consistent with the rated torque adjustment range of the coupling, ensuring that the torque setting is intuitive and accurate. Two sets of tapered roller bearings 4 with a relatively distributed layout are adopted. The inner wall raceway of the bearing 4 is inclined, and cylindrical rollers are rotatably installed inside. The two sets of bearings 4 are axially positioned by a positioning ring. The positioning ring is a ring structure and is fixed to the half coupling 1 by 6 M8 bolts. Its end face is tightly fitted with the inner ring of the bearing 4 to ensure that the coaxiality of the bearing 4 is small after assembly. The clearance between the inner wall of the transition flange 5 and the outer ring of the bearing 4 is small to ensure that there is no radial runout during transmission.

[0036] The diaphragm assembly 6 adopts a stacked structure with 12 slots arranged in a ring array for assembly with connecting bolt 2. It can effectively absorb coaxiality deviation during installation and impact vibration during operation. The insulating plate 9 is set between the connecting flange and the second half-coupling 2. It is made of epoxy resin glass cloth and can achieve electrical insulation between the first half-coupling 1 and the second half-coupling 2, avoiding damage to the equipment caused by static electricity or leakage during transmission. The connecting flange is a Q235 steel machined part. It is fixed to the intermediate section 7 by 8 M10 drive bolts 8 and nuts, and fastened to the second half-coupling 2 by 6 M8 connecting bolts 1 to ensure connection strength.

[0037] The signal trigger 10 uses a Hall displacement sensor, which is fixed on the side bracket of the half coupling 1. The distance between the sensor probe and the rear end of the column 15 of the ejector module 3 is 2-3mm. The working status of the ejector module 3 is determined by monitoring the axial displacement of the column 15. The output of the signal trigger 10 is connected to the control system through a shielded cable. It can output a 24V DC signal at the moment of overload disconnection, which is used to start the sound and light alarm device or trigger the emergency stop of the drive motor.

[0038] Insert the disc spring 12 into the sliding groove of the outer shell 11, ensuring that the openings of the disc springs 12 are aligned and face the extrusion block. After stacking the two disc springs 12, pre-compress them and check that the disc springs 12 slide freely in the sliding groove without jamming. Insert the extrusion block into the outer shell 11, with its inclined surface facing the inside of the outer shell 11 and fitting against the end face of the disc spring 12. Push the extrusion block by hand to ensure that it moves smoothly along the axial direction of the sliding groove. Place the small ball bearing 13 on the inclined surface of the extrusion block, add a small amount of lithium-based grease, and rotate the small ball bearing 13 to ensure that it rotates freely without jamming. Insert the column 15 into the outer shell 11, with its front end fitting against the small ball bearing 13 and its rear end extending beyond the end face of the outer shell 11. Check the axial movement of the column 15; there should be no deviation or jamming during movement. Cover the opening of the outer shell 11 with the end cap 16, align it with the mounting hole five, and screw in four M6 hexagon socket bolts, using a torque wrench to apply 8N. Tighten the torque of m, and at the same time install the dial, align the zero position of the dial with the initial position of the cylinder 15, and make a mark. Adjust the pre-compression of the disc spring 12 by rotating the end cover 16, and set the initial disengagement torque. During the adjustment process, use a torque tester to detect in real time to ensure that the torque setting is accurate. After the adjustment is completed, apply thread locking agent at the connection between the end cover 16 and the outer shell 11 to prevent loosening.

[0039] Apply a uniform layer of lithium-based grease to the annular groove of the transition flange 5. Install the two sets of tapered roller bearings 4 into the annular grooves, ensuring that the outer rings of the bearings 4 fit tightly against the annular grooves without any looseness. Apply lithium-based grease to the annular groove on the end wall of the half-coupling 1. Place the locating ring against the end face of the half-coupling 1, align it with the mounting hole 4, and screw in 6 M8 bolts. Press 15N. Tighten the torque to m, ensuring the end face of the positioning ring is perpendicular to the end face of half-coupling 1. Insert the positioning mandrel into the shaft hole of half-coupling 1. Using the positioning mandrel as a reference, fit the transition flange 5 onto the end of half-coupling 1, making the inner ring of bearing 4 fit against the end face of the positioning ring. Ensure the transition flange 5 is coaxial with half-coupling 1. Use a dial indicator to check the radial runout of transition flange 5. If it exceeds the tolerance, adjust the position of transition flange 5 until it meets the requirements. Install the large ball 14 into the mounting hole of the large ball 14 of transition flange 5, and add a small amount of lithium-based grease to ensure the large ball 14 rotates flexibly. Distribute the 8 pre-assembled pin modules 3 evenly along the annular end face of half-coupling 1, align them with the mounting holes, and screw in the fixing bolts. Press 12N. Tighten the torque of m, adjust the front end of the column 15 of the ejector module 3 to fit with the large ejector ball 14 of the transition flange 5, fine-tune the torque setting value of each ejector module 3 through the dial to ensure that the disengagement torque of the 8 modules is consistent, and tighten the dial fixing screw after the adjustment is completed.

[0040] Place the diaphragm assembly 6 between the mating surfaces of the transition flange 5 and the intermediate section 7, align it with mounting hole three, insert connecting bolt two, fit in the flat washer and spring washer, and tighten the nut using a torque wrench to 25N. The torque of m is used for cross-tightening to ensure that the diaphragm assembly 6 is subjected to uniform force and without twisting deformation. The radial runout of the intermediate section 7 is checked with a dial indicator. If it exceeds the tolerance, the position of the diaphragm assembly 6 is adjusted or the diaphragm assembly 6 is replaced. The connecting flange 5 is fitted into the end of the intermediate section 7, aligned with the first mounting hole, the drive bolt 8 is inserted, and the drive nut is screwed in. It is ensured that the connecting flange 5 and the intermediate section 7 are coaxial. The insulating plate 9 is placed between the connecting flange 5 and the second half coupling 2, aligned with the second mounting hole, and the connecting bolt 1 is screwed in. During the tightening process, the insulating plate 9 is checked for any displacement or damage.

[0041] Fix the signal trigger 10 to the side bracket of the half coupling 1, adjust the distance between the sensor probe and the rear end of the column 15 of the ejector module 3, fix the probe position with the lock nut, connect the power line and signal line of the signal trigger 10, check that the line connection is firm and there is no short circuit or open circuit, tidy up the line and fix it with cable tie to avoid tangling during operation, install the assembled coupling on the test platform, use a dial indicator to check the coaxiality of the active end and the passive end, if it exceeds the tolerance, correct it by adjusting the position of the transition flange 5 or the connecting flange, use a torque tester to load test the coupling, gradually increase the input torque, record the torque value at the moment of disengagement, compare it with the set value, if it exceeds the tolerance, fine-tune the pre-compression of the disc spring 12 of the ejector module 3 through the dial until the requirements are met;

[0042] During the torque test, a multimeter was used to check the output signal of the signal trigger 10, ensuring a 24V DC signal was output at the instant of overload disconnection, with a signal duration of 1 second, and no delay or distortion. Simultaneously, the triggering effect of the signal on the alarm device and shutdown control was tested to ensure reliable operation. The coupling was installed on the test bench, and all components were checked for smooth operation and no abnormal noise. After shutdown, all bolts were checked for looseness, and the ejector pin module 3 was checked for displacement. Ten consecutive overload disconnection tests were performed, with each overload torque being 1.2 times the set value. The disconnection response time, residual torque, and reset status were recorded for each disconnection, ensuring a response time ≤ 5ms and a residual torque ≤ 5N. m, after reset, the torque setting value remains unchanged, the signal feedback is stable, the pin-type torque limiting safety coupling achieves torque limitation through the locking and disengagement mechanism of the mechanical structure, combined with the signal feedback function, taking into account both mechanical safety and electrical safety, its working principle can be divided into three stages: normal transmission, overload disengagement, and reset and commissioning.

[0043] When the equipment is in normal operation, the drive shaft drives the half-coupling 1 to rotate. Under the pre-compression force of the disc spring 12, the eight sets of ejector pin modules 3 evenly distributed on the half-coupling 1 tightly press the front end of the column 15 against the large ejector ball 14 in the transition flange 5, forming a rigid locking structure. At this time, the torque transmission path is: drive shaft → half-coupling 1 → ejector pin module 3 (column 15 → large ejector ball 14) → transition flange 5 → diaphragm group 6 → intermediate section 7 → connecting flange → half-coupling 2 → load shaft, realizing synchronous transmission between the active and passive ends. During the transmission process, the diaphragm group 6, with its elastic deformation capability, effectively absorbs the coaxiality deviation, angular deviation, and axial deviation generated during the installation process, avoiding additional deviations caused by the deviation. Torque protection for all transmission components: Insulation plate 9 electrically isolates half-coupling 1 (driving end) from half-coupling 2 (passive end) to prevent static electricity accumulation or leakage during transmission, ensuring electrical safety of the equipment; Signal trigger 10 monitors the position of column 15 of pin module 3 in real time. At this time, column 15 is in the extended and locked state, the sensor has no signal output, and the coupling continues to transmit stably. Compared with traditional hydraulic safety couplings, the torque transmission of this structure does not rely on the pressure of hydraulic oil and is not affected by changes in ambient temperature. The evenly distributed design of 8 pin modules 3 makes the torque transmission more uniform and the control accuracy higher, solving the problem of inaccurate torque control caused by temperature and pressure fluctuations in hydraulic couplings.

[0044] When abnormal situations such as sudden load changes or jamming occur during equipment operation, and the input torque exceeds the preset disengagement torque of the coupling, the overload torque is transmitted to the column 15 of the ejector module 3 through the large ball 14 of the transition flange 5. The axial thrust on the column 15 increases rapidly. When the thrust is greater than the pre-compression elastic force of the disc spring 12, the disc spring 12 begins to compress and deform. The extrusion block moves backward along the sliding groove of the outer shell 11. Since the contact surface between the extrusion block and the small ball 13 is an inclined plane, as the extrusion block moves, the small ball 13 rolls along the inclined plane, generating a radial component force, which pushes the column 15 to retract rapidly.

[0045] When the retraction of column 15 reaches 10mm, the front end of column 15 completely disengages from the large ball 14 of transition flange 5, and the locking state of ejector module 3 is released. At this time, half coupling 1 (active end) and transition flange 5 (passive end) are completely disengaged, and the transmission chain is interrupted. Due to the synchronous operation of the 8 sets of ejector modules 3, the disengagement process is ensured to be smooth and without impact load. After disengagement, the active end only drives the ejector module 3 to rotate freely, while the transition flange 5 and subsequent passive ends stop rotating. Even if the active end continues to operate for a long time, the passive end will not follow the rotation, completely avoiding overload damage to the core components. At the instant of column 15 retraction, the Hall sensor of signal trigger 10 detects the axial position of column 15. Upon change in load, a 24V DC signal is immediately output. This signal can achieve two functions through the control system: first, to activate the audible and visual alarm device to promptly remind the operator that the equipment has an overload fault; and second, to trigger the emergency stop circuit of the drive motor, causing the drive motor to stop running within 1 second to prevent the overload condition from continuing to expand. Compared with friction-type safety couplings, this structure has no frictional wear after disengagement, does not require replacement of friction plates, and has extremely low residual torque. It solves the problems of torque attenuation and frequent maintenance caused by wear in friction-type couplings. Compared with break-type safety couplings, this structure can achieve overload protection without breaking any parts, avoiding the disadvantages of break-type couplings that are used only once and require replacement of spare parts.

[0046] Once the overload fault is cleared, the entire coupling can be quickly reset and put back into service without disassembling the entire machine. The operator only needs to rotate the end cover 16 clockwise using the dial on the end cover 16 of the ejector module 3. This moves the compression block forward, the disc spring 12 returns to its pre-compression state, and the small ejector ball 13 pushes the column 15 out until the front end of the column 15 presses against the large ejector ball 14 of the transition flange 5 again, forming a locking structure. At this time, the disengagement torque setting value is calibrated using the dial to ensure consistency with the initial setting. The reset process only takes 1-2 minutes, significantly reducing equipment downtime.

[0047] After resetting, the equipment is restarted, and the coupling resumes normal transmission function. The column 15 of the pin module 3 remains locked, the signal trigger 10 stops outputting alarm signals, and the equipment enters a stable operation phase. Since the coupling experiences no component damage or frictional wear during overload disengagement and does not use easily consumable media such as hydraulic oil or lubricating oil, it requires no regular maintenance, no replacement of spare parts, or special maintenance tools during long-term operation, achieving complete maintenance-free operation and significantly reducing equipment maintenance costs. The pin-type torque limiting safety coupling achieves advantages such as precise torque control, fast response speed, small residual torque, maintenance-free operation, no pollution, and convenient reset through the integrated mechanical and electrical design of "disc spring 12 preload - inclined plane force transmission - synchronous disengagement - signal feedback". Compared with hydraulic, friction, and break-type safety couplings, it has significant advantages in terms of safety, reliability, and economy.

[0048] Example 2:

[0049] A connecting flange is provided between the intermediate section 7 and the second half coupling 2. The connecting flange and the inner side of the intermediate section 7 are provided with mounting holes arranged in a ring array. A drive bolt 8 is installed inside the mounting hole 1, and a drive nut is threaded onto the outer wall of one end of the drive bolt 8.

[0050] An insulating plate 9 is provided between the connecting flange and the second half coupling 2. The second half coupling 2 and the second connecting flange are both provided with mounting holes 2 arranged in a ring array. A connecting bolt 1 is screwed into the thread of the mounting hole 2.

[0051] A bearing 4 is provided between the coupling and the transition flange 5. The bearing 4 is arranged in two sets with a relatively distributed layout, and the inner wall raceway is inclined. Columnar rollers are rotatably installed inside the inclined raceway.

[0052] The inner side of the intermediate section 7 where it meets the transition flange 5 is provided with mounting holes three arranged in a ring array, and two connecting bolts are installed inside the mounting holes three.

[0053] A diaphragm assembly 6 is provided between the intermediate section 7 and the transition flange 5. The diaphragm assembly 6 is annular and has corresponding mounting holes 3 on its side for connecting bolts 3 to be assembled.

[0054] In this embodiment, the intermediate section 7 and the second half-coupling 2 are rigidly connected by a connecting flange. The connecting flange and the edge of the intermediate section 7 are evenly distributed with annular array mounting holes 1, and the built-in drive bolts 8 and self-locking drive nuts ensure connection strength and assembly adjustability. An insulating plate 9 is added between the connecting flange and the second half-coupling 2, and an insulating washer is used to achieve complete electrical isolation, blocking static electricity and leakage conduction. Two sets of oppositely distributed tapered roller bearings 4 are used between the first half-coupling 1 and the transition flange 5. The inner wall inclined raceway is matched with columnar rollers, which can bear radial and axial loads at the same time, and the transmission friction coefficient is low. The intermediate section 7 and the transition flange 5 are fastened by annular array mounting holes 3 and connecting bolts 2. The contact surface is provided with a stacked 316L stainless steel diaphragm group 6. The slot design reserves elastic deformation space, which can absorb installation deviation and impact vibration, and ensure smooth transmission. Through modular connection design, reliable electrical isolation and flexible compensation structure, both connection rigidity and operational safety are taken into account. It is suitable for chemical, power and other working conditions with strict requirements for electrical protection and load stability.

[0055] Example 3:

[0056] Both the inner wall of the transition flange 5 and the outer wall of one end of the half coupling 1 are provided with annular grooves for assembling the bearing 4. A positioning ring located inside the transition flange 5 and in contact with the inner ring of the bearing 4 is provided on one side of the half coupling 1.

[0057] The positioning ring and the half coupling 1 both have mounting holes 4 arranged in a ring array inside, and bolts 3 are screwed into the threads inside the mounting holes 4.

[0058] The inner wall of the outer shell 11 is provided with symmetrically distributed sliding grooves for assembling the disc spring 12. One end of the disc spring 12 is provided with a pressing block that fits with the small top bead 13. The side of the pressing block that fits with the small top bead 13 is inclined, and the side of the small top bead 13 that fits with the outer wall of the bead is inclined.

[0059] An end cap 16 is provided at the opening of the outer shell 11 and is slidably assembled with the column 15. Both the end cap 16 and the inner surface of the outer shell 11 are provided with five mounting holes arranged in a ring array. Four bolts are screwed into the five mounting holes.

[0060] In this embodiment, both the inner wall of the transition flange 5 and the end of the half-coupling 1 are provided with special annular grooves for precise assembly of the bearing 4. These grooves, along with a custom positioning ring, are fastened to the half-coupling 1 via mounting holes 4 and bolts 3, ensuring a tight fit between the inner ring of the bearing 4 and the outer shell 11. The inner wall of the ejector module 3 housing 11 has symmetrical sliding grooves to accommodate large-size symmetrical disc springs 12. Force is transmitted through the compression block and small ejector ball 13. Both surfaces are designed as bevels, and the spherical contact structure improves force uniformity and wear resistance. A thickened end cap 16 is fitted at the opening of the housing 11. The five mounting holes and four bolts are tightened, and a copper alloy guide sleeve is added to the inside to form a high-precision sliding fit with the column 15, ensuring that the axial movement of the column 15 is smooth and without jamming. The end cover 16 integrates a high-precision dial, which supports stepless adjustment of the disengagement torque. It works with the signal trigger 10 to monitor the displacement in real time and quickly outputs a 24V DC signal when overloaded. Through precision assembly positioning, optimized force structure and precise adjustment design, it achieves a unity of high reliability and convenient operation, and is especially suitable for mechanical manufacturing scenarios with high requirements for torque control accuracy and continuous operation of equipment.

[0061] The above specific embodiments are merely several preferred embodiments of the present invention. Based on the technical solutions of the present invention and the relevant teachings of the above embodiments, those skilled in the art can make various alternative improvements and combinations to the above specific embodiments.

[0062] It will be apparent to those skilled in the art that the present invention is not limited to the details of the exemplary embodiments described above, and that the invention can be implemented in other specific forms without departing from its spirit or essential characteristics. Therefore, the embodiments should be considered in all respects as exemplary and non-limiting, and the scope of the invention is defined by the appended claims rather than the foregoing description. Thus, all variations falling within the meaning and scope of equivalents of the claims are intended to be included within the present invention. No reference numerals in the claims should be construed as limiting the scope of the claims.

Claims

1. A quick-adjustable torque-limiting safety coupling, comprising a first half-coupling (1), a second half-coupling (2), a pin module (3), a transition flange (5), and an intermediate section (7), characterized in that: The first half-coupling (1) has a transition flange (5) on one side, an intermediate section (7) on one side of the transition flange (5), a second half-coupling (2) on one side of the intermediate section (7), a pin module (3) arranged in a ring-shaped column distribution inside the side of the first half-coupling (1), a large pin ball (14) arranged in a ring-shaped array inside the pin module (3) corresponding to the transition flange (5), the pin module (3) includes a housing (11), a disc spring (12) symmetrically distributed on the side of the housing (11), a lower pin ball on one side of the disc spring (12), a column (15) located inside the housing (11) and located at one end of the large pin ball (14) and in contact with the small pin ball (13), and a signal trigger (10) arranged on one side of the first half-coupling (1) and on one side of the pin module (3).

2. The quick-adjustable torque-limiting safety coupling according to claim 1, characterized in that: A connecting flange is provided between the intermediate section (7) and the second half coupling (2). The connecting flange and the inner side of the intermediate section (7) are provided with mounting holes arranged in a ring array. A drive bolt (8) is installed inside the mounting hole. A drive nut is threaded onto the outer wall of one end of the drive bolt (8).

3. The quick-adjustable torque-limiting safety coupling according to claim 2, characterized in that: An insulating plate (9) is provided between the connecting flange and the second half coupling (2). The second half coupling (2) and the second connecting flange are both provided with mounting holes arranged in a ring array. A connecting bolt is screwed into the second mounting hole.

4. The quick-adjustable torque-limiting safety coupling according to claim 1, characterized in that: A bearing (4) is provided between the coupling and the transition flange (5). The bearing (4) is arranged in two sets of relatively distributed layouts, and the inner wall raceway is inclined. Columnar rollers are rotatably installed inside the inclined raceway.

5. A quick-adjustable torque-limiting safety coupling according to claim 1, characterized in that: The middle section (7) and the transition flange (5) are fitted with mounting holes arranged in a ring array, and the mounting holes are fitted with connecting bolts.

6. A quick-adjustable torque-limiting safety coupling according to claim 5, characterized in that: A diaphragm assembly (6) is provided between the intermediate section (7) and the transition flange (5). The diaphragm assembly (6) is annular and has corresponding mounting holes for connecting bolts.

7. A quick-adjustable torque-limiting safety coupling according to claim 1, characterized in that: The inner wall of the transition flange (5) and the outer wall of one end of the half coupling (1) are both provided with annular grooves for assembling the bearing (4). A positioning ring located inside the transition flange (5) and in contact with the inner ring of the bearing (4) is provided on one side of the half coupling (1).

8. A quick-adjustable torque-limiting safety coupling according to claim 7, characterized in that: The positioning ring and the half coupling (1) are both provided with mounting holes (4) arranged in a ring array, and bolts (3) are screwed into the mounting holes (4).

9. A quick-adjustable torque-limiting safety coupling according to claim 1, characterized in that: The inner wall of the outer shell (11) is provided with symmetrically distributed sliding grooves for assembling the disc spring (12). One end of the disc spring (12) is provided with a pressing block that fits with the small top bead (13), and the side of the pressing block that fits with the small top bead (13) is inclined. The side of the small top bead (13) that fits with the outer wall of the bead is also inclined.

10. A quick-adjustable torque-limiting safety coupling according to claim 1, characterized in that: The opening of the outer shell (11) is provided with an end cap (16) that is slidably assembled with the column (15). Both the end cap (16) and the outer shell (11) have five mounting holes arranged in a ring array inside. Four bolts are screwed into the mounting holes.

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