FORM-2
THEPATENT ACT, 1970
(39of 1970)
COMPLETE SPECIFICATION
Title:
A FLEXIBLE COUPLING WITH RESILIENT MEANS FOR TORQUE
TRANSMISSION WITH OPTIMIZED TORSIONAL STIFFNESS
(a) Applicant Name: Elecon Engineering Company Ltd.
(b) Nationality:lndian
(C)Address- Elecon Engineering Co. Ltd. AnandSojitra Road VallabhVidyanagar - 388120 Gujarat, India.
The following specification particularly describes and ascertains the nature of this
invention and the manner in which it is to be performed.
COMPLETE

Technical Field
[0001] The present patent application relates to a flexible coupling with resilient means for torque transmission with optimized torsional stiffness. More particularly present invention provides coupling with rubber ring and easy assemble means for quick change at the time of maintenance.
Background
[0001] Flexible couplings are one of the major types of couplings. They find use to connect two shafts, end-to-end in the same line to transmit power that is torque from one shaft to another, thereby causing both to rotate in unison, at the same rpm. The other purpose is to compensate for small amounts of misalignment and random movement between the two shafts. Several factors should always be taken into consideration when looking to specify flexible couplings.These are torsional stiffness, backlash, torque, life, and attachment system. All of these have bearing on coupling selection. Specific details vary depending on the different types and their functions.
[0002] The purpose of a flexible coupling is to transmit torque from one piece of rotating equipment to another, while accepting at the same time a small amount of misalignment. Flexible coupling misalignment is expressed, as an order of magnitude, in thousands of an inch. Actual misalignment, expressed in coupling terms, is angular in nature and expressed in angular units, that is, degrees. An installation variable is the equipment movement due to the temperature changes taking place in the machines as they go from the non-operating state to operation. Some angular values will be used in the discussion of the various types, but, again, these are for reference only. Each

application must be reviewed using the type of coupling selected and the specific design proposed by the vendor.
[0003] Flexible couplings of the kind specified are widely utilized, for example, in drive lines in machine. The nature of the flexible element is such that some misalignment between the coupled rotary elements can be tolerated, and possibly also some relative axial movement there between. The most usual form of the flexible element has been a disc or annulus made of a fabric or an elastomeric material, which performs satisfactorily but has disadvantages in respect of its torque transmitting capacity for a given size and weight. Such relative torque transmitting capacity could be improved if the flexible element could be made of a fiber reinforced plastics material of the kind now used in many applications for springs, but a simple disc or annulus of such material when used in a coupling of the kind specified lacks torsional flexibility although it may be sufficiently flexible to accommodate some misalignment (articulation) between the rotary elements.
[0004] In many machines, it is desirable to vary the alignment of shafts and the like in power trains transmitting rotary motion from a prime mover to a final point of output, thus requiring flexible couplings. The driving and driven members on opposite sides of such couplings may be displaced angularly, radially, or longitudinally with respect to each other. In many instances, it is not to improvements in power transmission couplings, and particularly to flexible coupling means used to transmit power from a driving member to a driven member, for example, a pair of substantially co-axial power shafts.

[0005] Certain prior art couplings have embodied a solid resilient element to transmit torque and to compensate for the misalignment of the input and output shafts. Such couplings are not adequate for heavy-duty apparatus because when high torque is transmitted the resilient member must be relatively thick to withstand the high stresses involved. Therefore, flexibility is sacrificed. In certain other prior art devices, the torque has been transmitted through a hollow, flexible element having walls sufficiently thin to provide the required degree of flexibility but insufficiently supported internally. Such devices have tended to collapse and even rupture under high torque.
[0006] Certain particular flexible couplings have been manufactured in the past so as to include two hubs or hub elements which are adapted to be connected to the shafts joined by the coupling. These hubs are each provided with extending lugs, teeth, or ribs serving as holding means so as to be engaged by corresponding projections on a band-like or belt-like motion transmitting means in order to cause the hubs to rotate in synchronism as one of the shafts is rotated. The bands or belts used in these prior couplings have been flexible, somewhat resilient belts capable of being wrapped around the hubs so that the projections on them engage the holding means on the hubs.
[0007] Elastic couplings having elastomeric elements, for example pursuant to DE3910502C2, transmit the torque by means of a peripheral force that primarily subjects the elastomeric elements to bending and pressure. In order at a prescribed structural size to be able to transfer as great a torque as possible, the elastomeric element must be as hard as possible. On the other hand, the staggered shaft arrangement of the coupled mechanisms leads to a deformation of the elastomeric element. Similarly, the requirement of having a low restoring force, and hence the

requirement of having low additional bearing forces of the coupled mechanisms, call for elastomeric elements that are as soft as possible. In addition, the hardness of the elastomeric element essentially determines the torsional spring rigidity of the coupling. Here too there often exists the requirement for a configuration having low torsional stiffness with correspondingly high dampening.
[0008] Flexible couplings are used to transmit rotational forces between two non collinear shafts, the rotational axis of which intersect approximately in the centerof the coupling. "Rotational axis" refers to the axis about which the shaft rotates. The non-collinear orientation of the coupled shafts described above is referred to as "angular misalignment".
[0009] Typical flexible coupling assemblies embody attachment means for attaching the coupling to the driving and driven shafts respectively. At least one load transmitting element is used to transmit forces between the respective attachment means despite angular misalignment of the two shafts.
[00010] Prior flexible couplings have used either rigid or resilient load transmitting elements. Typical rigid load transmitting elements comprise a rod or rocker having bearing surfaces at both ends which permit the element to rock or pivot, relative to the attachment means, in response to angular misalignment of the driving and driven shafts. A disadvantage with this type of load transmitting element is that it will develop free play and, unless the motion along the axis ("axial motion") of the respective attachment means is constrained, torque applied to this type of coupling will cause it to disassemble.

[00011] In order to provide a constraint against the tendency to disassemble anddevelopment of free play inherent in couplings having rigid load transferringelements, couplings have been developed which utilize a resilient material between conforming surfaces of the attachment means as transmitting elements.A disadvantage with resilient load transmitting elements is that if they are to belarge enough to withstand large torque loads, excessive resistance to angularmisalignment arises due to the forces required to deform the resilient elements toflex the coupling.
[00012] In a flexible coupling serving as a shaft connector, it is essential to provide sufficient flexibility of connection between the coupled shafts, to compensate for unavoidable misalignment of the shafts. It is also essential to provide sufficient torque-carrying capacity, between the connected elements, to withstand adequately all possible overload torques. In the older prevailing types of couplings, in order to increase the torque-carrying capacity of the coupling, the flexibility has been, decreased to such an extent that the coupling practically constituted a rigid device, which condition exposed the coupled shafts to dangerously excessive deflections and stresses. Further, such an arrangement of coupled shafts, destroyed the shock absorbing capacity of the flexible means, to cope with sudden overload torques
[00013] The flexible coupling use a resilient material to transmit torque between two metallic hubs. Elastomeric couplings obtain their flexibility from stretching or compressing a resilient material such as rubber, and plastic. Some sliding or rolling may take place, but it is usually minimal.
[00014] The design of elastomeric couplings means that the elastic materialis meant to wear out before any metal components. This not only saves time and money

on maintenance but also means that the couplings do not require lubrication. An advantage of this coupling are the high vibration dampening, shock absorption abilities, and toleration of a high degree of misalignment. They are also inexpensive and of lighter weight than mechanical couplings. The elastomeric element is sufficiently resistant to fatigue failure to provide an acceptable life compared to the cost of the coupling.
[00015] The function of a flexible coupling is to transmit torque from the driver to the driven machine while making allowances for minor shaft misalignment and shaft end position changes between the two machines. The design of the coupling should provide for transmission of the required torque at the required speed with a minimum of extraneous forces and perturbations exerted on either the driver or driven shaft. Shaft misalignment exists when the centerlines of two shafts joined by a coupling do not coincide.
[00016] A few examples of such flexible sleeve couplings can be seen in U.S. Pat. Nos. 2,867,102 and 2,867,103 (the Williams references), which issued in 1956 and 1957, respectively, and describe a flexible coupling for shafts and a gripping arrangement for flexible couplings for power transmission shafts.
[00017] One known issue or limitation of known flexible sleeve couplings is that, during high torque or shock loading situations, the teeth along the outer and inner diameter of the sleeve element deform and roll underneath the opposing teeth of the connected hubs. In extreme conditions, such deformation results in an interruption in torque transmission when the teeth of the flexible element either shear off the element entirely or eject the element from the connected hubs. It has been proposed in the past

to increase the stiffness of the elastomeric material such that higher torque loads can be carried. However, such stiffness increases, while possibly better suited to withstand higher torque loads than the baseline stiffness flexible sleeves, decrease the sleeve's flexing ability and, therefore, the coupling's ability to withstand misalignment.
OBJECT OF INVENTION
[00018] The prime object of the present invention is to provide a flexible coupling with resilient means for torque transmission with optimized torsional stiffness.
[00019] An object of the present invention is to provide an improved coupling, possessing increased flexibility, improved capacity for absorbing torsional shocks without damage, and embodying means enabling an alteration of critical torsional speeds to damp out undue vibrations.
[00020] A further object of the invention is to provide an improved coupling, embodying means for reducing the transmission of torsional vibration, or for damping the effect of vibrations produced in one coupled rotating mass, and minimizing the transmission of such vibrations to the other coupled rotating mass.
[00021] Another object of the present invention is to coupling that makes it possible to compensate for an axialdisplacement and a radial displacement of the axes of rotation of the machine parts coupled toone another and is furthermore characterized by a particularly compact design, so that it canperform its functions even in very limited installation space conditions.
[00022] Yet another object of the present invention is to provide flexible coupling with rubber ring having fabric lining at regular interval that provides advanced shock absorption and adaptable to misalignment in operation.

[00023] Further object of the present invention is to provide flexible coupling with quadruple grip rubber ring arrangement located between the junction of drive and driven hubs by fastening criss-cross fasteners arrangement.
[00024] Yet another object of the present invention is to provide flexible coupling having rubber ring arranged with criss cross through mediator ring between two hubs.
[00025] Yet another object of present invention is to provide flexible coupling having easy and fastassembling-dissembling means during maintenance that directly correlated to down time in the system.
SUMMARY
[00026] The present invention provides a flexible coupling with resilient means for torque transmission with optimized torsional stiffness. The flexible coupling includes two hubs, each hub configured to engage a shaft along a central portion and engage alongafastening means. The flexible coupling further includes a resilient means disposed between the two hubs engaged relation with mediator ring between the engagement portions of each of the two hubs. The resilient means generally includes rubber ring with two pairs of half circular rubber rings having arch shape arranged to fasten between mediator ring and two hubs, to provide maximum shock absorbance and minimize damping effect. The present invention provides slanted portion of hub (2) and rubber ring (6) with fabric lining that enhance axial misalignment and optimized torsional stiffness.The coupling (1) with flexible rubber ring (6) transmits power with flexibility in terms of axial, radial and angular misalignments. It also provides damping effect to the transmission, which helps to reduce the transmission prompted vibrations. This is possible due to flexible rubber ring. This coupling has advantage of easy

assembling and dissembling, even in very limited installation space conditions, which minimize the down time during maintenance.
BRIEF DESCRIPTION OF THE DRAWINGS
[00027] The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate disclosed embodiments and, together with the description, serve to explain the disclosed embodiments. In the drawings:
[00028] FIG. 1 illustrates side sectional view of the coupling (1) according to present invention
[00029] Fig. 2 illustrates exploded perspective view from the driven hub (3) of the coupling (1) according to present invention
[0030] Fig. 3 illustrates exploded perspective view from the drive hub (2) of the coupling (1) according to present invention
[0031] Fig. 4 illustrates perspective side view of the coupling (1) in anassembled mode
[0032] Fig. 5 illustrates cross sectional side view of drive hub (2) according to present invention
[0033] Fig. 6 illustrates cross sectional side view of intermediate metal ring (4) according to present invention
[0034] Fig. 7 illustrates cross sectional side view of driven hub (3) according to present invention
[0035] Fig. 8 illustrates cross sectional side view rubber ring (6) in one half according to present invention

[0036] Fig. 9 illustrates simulation test results for directional deformation on different flexible rubber ring cross-section trials
[0037] Fig. 10 illustrates simulation test results forVon-Misses Stresses on different flexible rubber ring cross-section trials
Detailed Description
[0038] Fig. 1 illustrates side sectional view of the coupling (1) according to present invention where in a drive hub (2) and a driven hub (3) connect through an intermediate metal ring (4) accompanied with a supportive metal rings (5, 7, 8) and a pair of rubber rings (6). The drive hub (2), described in details in Fig. 5, located at one in the system where drive shaft is situated. At one end the drive shaft (2) has cylindrical portion (14) where inside the hollow portion key (22) to get locked with the drive shaft in the system. The cylindrical portion (14) is followed by gradually slant face (13) and straight fagade (12). The fagade (12)connects over lateral face of metal ring(4) though fasteners (11). The Multiple holes 15 are available on slant face (13) to facilitate air circulation inside the coupling (1).
[0039] The metal ring (4), at one end, connected with lateral face of hub (2) through fasteners (11). The fastening means (11) fasten the metal ring (4) and drive hum (2) through matching holes in respective components. The said junction primary provides power transmission channel at one end. The invention indirectly shifts major power transmission dependency to rigid component to resilient conjugation of rubber in the present invention.
[0040] The metal ring (4) is hollow ring having steps inside to accommodate rubber rings in the system. The metal ring (4) play vital role in arrangement of coupling

(1) as it's not only connect the drive hub (2) and driven hub (3) passively through rubber rings but also provides easy assembling-dissembling in the coupling without further removing whole coupling from the installed system. The metal ring (4) holds fastening means at one end (23) of periphery where fasteners (11) were accommodated inside. The lowest step (24) of the metal ring (4) accommodates fastening ring (5) along with fasteners. The said arrangement of bolts (9) clearly as periphery bold depicted in the Fig. 4. The intermediate step (25) provides fit accommodation to pair of rubber ring (6). The inner most step (26) provides space to accommodate half rubber ring (6) and inner part of driven hub (3).
[0041] The driven hub (3) has mainly three parts with stepped arrangement to accommodate specific allied component in the system. The hub contains provision for key (21) to hold driven side assembly shaft inside. The lower plan (20) has extended portion to be accommodate the driven unit inside in the system. The point of step (19) provides support for metal ring (7) with fastening bolt. The flange (17) and upper plan (18) accommodates pair of rubber ring (6) with intermediate metal plate (8).
[0042] The stacked arrangement of rubber ring (6) with means of fasteners and plate is depicted in the Fig. 2 and 3 where exploded view of each presented clearly. As discussed earlier, the scope of present invention lies in the cross arrangement of drive and driven hub with rubber ring. In order to fulfill the object of torsional stiffness present invention discloses unique power transmission in advanced ay where rubber intermediately provides shock absorber though its intrinsic behaviors and Kevlar lining arrangement. The detailed depiction of rubber ring (6) provided in Fig. 8. It is to be noted that rubber ring (6) has been divided into four parts for easy access during

maintenance but the same can be divided into three or two parts for each half circular ring.
[0043] The present invention provides rubber ring stacked arrangement that provides a flexible coupling serving as a shaft connector, further it also provide sufficient flexibility of connection between the coupled shafts,to compensate for unavoidablemis-alignment ofthe shafts. It is also essential to provide sufficient torque-carrying capacity between the connected elements, to withstand adequately all possible overload torques.
[0044] The present coupling provides unique arrangement of metal ring (4) alongwith rubber ring (6) intermediately positioned between drive hub (2) and driven hub (3), and alternative arrangement ofclamping pair of half circular rubber ring upper end and lower ends of half circular rings (6) stacked with metal ring (8) and end portion of driven hub (3). The arrangement of present invention provides unique solution to state of the art couplingswhere in order to increase the torque carrying capacity of the coupling, the flexibility has been decreased to such an extent that the coupling practically constituted a rigid device. Due to the said rigidity when couplings were exposed to the overload condition, the coupled shafts exposed to excessive deflections and stress that amount to down time or maintenance in the system. Further, such an arrangement of coupled shafts,practically minimizes the shock absorbing capacity of the flexible means, to cope with sudden overload torques.
[0045] As depicted in Fig. 2-3 the arrangement of fastening means including fastening plate, bolt and fastening pin connecting drive-driven hub is complex arrangement that is described in exploded view in said figures.

[0046] As depicted in Fig. 2, drive hub has provision for fasteners (11) to accommodate from one of drive hub to rest at dedicated slots (23) provided in metal ring (4) at periphery of the ring. The half circular rubber ring (6) provided in stacked way that connected at upper end with fastening pin (9). The fastening pin located in periphery engaged with junction of half circular rubber rings (6) at one end and secularly fasten with fastening plate (7) and bolt (10) to provide specific fitment at the periphery of the coupling. The position of fastening plates (7, 8) and fasteners plays vital role in present invention as said cross arrangement is responsible for optimized torsionalstiffness, axial and radial flexibility against misalignment and easy replacement of rubber ring at the time of maintenance. Fig. 2-3 provides self-explanatory arrangement for the position and connection of each crucial component in the present coupling. It is submitted that Fig.(2-3) along with Fig. 1 provides clear explanation of the arrangement of half circular rubber ring (6) and its placement between driven and drive hubs (2,3).
[0047] The pair of rubber ring (6) conjugated at one end with fasteners (9) and clamped at second end with metal ring (5) through bolt.
[0048] The driven hub (3) is located opposite to drive hub (2) to accommodate shaft of to be driven machinery in the system. The hub has circular hollow area with provision for key (21) to get lock with shaft of driven side machine. The hub (3) consists of hollow cylinder (20) followed by hollow cylinder (19) which is slight step up arrangement at outside surface then hollow cylinder (20). The said step arrangement was made to provide support for placement of small metal ring (7) at bottom. Further hollow cylinder (19) followed by hollow cylinder (18) which is slight step up arrangement

at outside surface then hollow cylinder 19 and at the end flange (17) is disposed. The flange (17) located in close proximity with slanted face (13) and perforated hole (15). While at other side accommodate one half circular rubber ring (6) along with fastener (10) established in one end of lower end of half circular rubber ring (6), intermediate metal plate (8).The driven hub (3) contains various stepped portions (17), (18), (19) and(20) that are designed in stepped manner to accommodate other components over it, for easy and fast assembling.
[0049] The reason behind using slanted face (13) in hub (2) is to get more co¬axial space between hub (2) and hub (1), without much increase in total weight of the invention.
[0050] The geometry of rubber ring (6) has been generated progressively through different trials starting from straight shape as shown in figure 9-10, similarly given in under crux of invention part of patent document.Flexible rubber ring's (6) is made of natural rubber with multiple Kevlar fabric lining (36). The Number of Kevlar lining just shown for representation it does not limit the number of lining for any particular embodiments.
[0051] As discussed earlier, the composition and shape of the conjugated rubber ring plays crucial role to achieve specific object of the present invention. The shape and Kevlar lining described in the Fig. 8 justify the use of specific particulars. Applicant has triedand tested as per standards, different type of materials with compositions as given in table-1 to select material for rubber ring (6). The material with lowest hardness, highest elongation and highest tensile strength i.e. Sample 2 (Natural rubber + Kevlar fabric) chosen.

Table -1

Composition Hardness Elongation Tensile strength
Sample -1 NBR RUBBER + KEVLAR FABRIC 81 302 17.4
Sample -2 NATURAL RUBBER + KEVLAR FABRIC 78 350 21.4
Sample -3 NBR RUBBER + NYLON FABRIC 80 228 16.8
Sample -4 NBR RUBBER 80 239 18.4
[0052] The results of simulation study conducted for selection of cross-section for the flexible rubber ring. An advanced high end simulation tool Ansys Version 19.2 was utilized for the study.
[0053] Fig. 8 illustrates sectional diagram of half rubber ring (6) as particular embodiment of the present invention. Flexible rubber ring's (6) is made of natural rubber with multiple Kevlar fabric linings (36) along with its pocket structure (30, 31) and outer curve (29) collectively provides strength and flexibility when combining with the counter replica rubber ring staked with intermediate metal ring (8). It is submitted that the conjugated rubber ring (6) provides specific advantage of shock absorbance as it jointly results into pocket shaped with diamond geometry provided with combining upper arc of rubber ring portion (27) and fastening lower parts of runner ring (33) with fastening means. The resultant assembly provides specific advantage for power transmission in efficient way through resilient means and it provides optimized torsional stiffness in the system.
[0054] The coupling of the present invention has tested in practical world where following specification has been fixed:

• Prototype Running speed -1500 rpm
• Prototype Torque - 2750 Nm
• Prototype Power - 430 kW TEST PERFORMED:
The prototype testing of a coupling with flexible rubber ring was carried out.
Static torsion test to understand and measure torsional stiffness of the
coupling. The coupling was subjected to mechanical endurance test (Load
test) to test feasibility in actual operating conditions.
o Static Torsion Test:
Result:

Arm
Length
(mm) Weight
(Kg) Theoretical
Angle Of
Twist (deg.) Length
of arc, L
(mm) Observed
Angle Of
Twist
(deg.) Torsional Stiffness
(kN.m/rad)
Full load 500 570 4.224 12 4.3 37.33
75% bad 500 430 3.35 12.2 4.371 36.69
50% load 500 285 2.15 13.14 4.707 34.1
25% load 500 145 1.56 14.64 5.245 30.6
o Mechanical Endurance Test (Load Test)

Motor Motor speed (rpm) Duration Time Temp, of rubber ring in°C Observation
Power (kW)

Rubber ring Metal parts remarks
430 1500 4320 min. (72 Hrs.) Max. 36.6 Max. 37.1
(Design Power of prototype)

Min. 29.5 Min. 29.7 WORKING OK

[0055] As illustrated in Fig. 9-10, the flexible rubber ring connects the input with output for torque transmission with flexibility and damping effect due to its rubber material characteristics as well as geometry effect. Material characteristics were investigated through material testing, results of which are available in abovementioned table. The cross-section was refined and developed based on the deformation and stress acting on it. Trial-1 being straight edged fails to provide flexibility and offers more deformation at the bottom part, whereas the trail-2 provides lesser deformation still showing scope for refinement of geometry and the trial-3 shown very less deformation over the cross-section. The stresses also observed to be lower as we refined cross-section from trial 1 to 3.
[0056] It is observed that Kevlar rubber ring alongwith optimized shape provides best result in the present invention. The flexible coupling with resilient means for torque transmission with optimized torsional stiffness is the result of specific arrangement of stacked rubber ring fasten with unique arrangement and Kevlar rubber lining provided with specific shape of rubber rings. The shape of the rings and position with fastening means and metal ringcollectively provides more flexibility with vibration/ shock absorption, since the molding of rubber at particular shape involves the geometric characteristics.
[0057] Moreover, while illustrative embodiments have been described herein, the scope includes any and all embodiments having equivalent elements, modifications, omissions, combinations (e.g., of aspects across various embodiments), adaptations or alterations based on the present disclosure. The elements in the claims are to be interpreted broadly based on the language employed in the claims and not limited to

examples described in the present specification or during the prosecution of the application, which examples are to be construed as non-exclusive. Further, the steps of the disclosed methods can be modified in any manner, including by reordering steps or inserting or deleting steps. It is intended, therefore, that the specification and examples be considered as example only, with a true scope and spirit being indicated by the following claims and their full scope of equivalents.

We claim,
1. A flexible coupling with resilient means for torque transmission with optimized torsional stiffness comprising,
a drive hub coupling part (2), a driven coupling hub part (3), a metal ring (4), at least one resilient means (6), at least one fastening support plate (5, 7, 8) at least one fasteners (9, 10),
wherein a driven hub (3) consist provision for holding key (22) at one end and have gradually slanted intermediate portion (13), with perforating holes (15), disposing with straight facade (12),
wherein the metal ring (4) is hollow circular ring extended axially contains rim with fastening holes at one end to hold fasteners (11) with straight facade (12) portion of drive hub (2),
wherein the drive hub coupling part (2) contains provision for holding key (21) at inner side and stepped arrangement (18, 19) disposing into perpendicular flange (17) having provision for holding fasteners on outer side,
wherein the resilient means includes rubber ring (6) having perforations to accommodate fastening means in conjugation with fastening plate (5, 7, 8).
2. The flexible coupling with resilient means for torque transmission with optimized torsional stiffness as claimed in claim 1, wherein a drive hub coupling (1) fixed with metal ring (4) through fastening means at rim disposed at one end of the metal ring (4).
3. The flexible coupling with resilient means for torque transmission with optimized torsional stiffness as claimed in claim 1, wherein a metal ring (4) disposed

at intermediate connecting member between drive hub (2) and driven hub (3) via resilient member interlock arrangement through fastening means and fastening support plate (5, 7, 8).
4. The flexible coupling with resilient means for torque transmission with optimized torsional stiffness as claimed in claim 1, wherein the resilient member generally includes rubber ring (6) preferably in two half circular ring arrangement and corresponding shape to arrange in stacked manner between flange of drven hub (3), fastening support plate (5, 7, 8) and fasteners (9, 10).
5. The flexible coupling with resilient means for torque transmission with optimized torsional stiffness as claimed in claim 1, wherein rubber ring collectively provides positional and shape configured advantage against linier and angular misalignment against odd stresses.
6. The flexible coupling with resilient means for torque transmission with optimized torsional stiffness as claimed in claim 1, wherein the rubber ring (6) contains Kevlar lining (36) inside each half rubber ring that provide elevated strength and shock absorbance characteristic in the system.
7. The flexible coupling with resilient means for torque transmission with optimized torsional stiffness as claimed in claim 1, wherein metal ring (4), rubber ring (6), fasteners (9, 10) and fastening plate (5, 7, 8) configured to provides easy assemble-dissemble during maintenance.