CROSS-REFERENCE TO RELATED APPLICATIONS

[0001] This application claims the benefit of US provisional application no. 62/844,904, filed May 08, 2019, the contents of which are incorporated herein by reference in their entirety.

FIELD

[0002] The specification relates generally to isolation devices for use on accessory drives for engines, and in particular for use on accessory drives for hybrid engines that incorporate a motor-generator unit (MGU) or similar device.

BACKGROUND OF THE DISCLOSURE

[0003] For engines, and in particular vehicular engines, an isolator is typically provided on the accessory drive so as to reduce the natural frequency of the external torque load driven by the crankshaft of the engine to be below the peak input torque frequency over a selected range of operating conditions for the engine. In some isolators, in addition to providing one or more springs there is frictional damping that is provided, which inhibits the isolator from going into resonance. Damping can be effective for this purpose, however, it is important not to provide too much damping, since this can negatively affect the performance of the isolator is primary function of reducing the natural frequency of the external torque load.

[0004] However, in some situations, it would be advantageous for the isolator to have a greater amount of damping. It would therefore be advantageous to provide an isolator that has an increased amount of damping in certain situations, but without having to have the increased amount of damping at all times. [0005] Separately, it is generally desirable for the isolator to have as much travel as possible, in some situations, while having a reduced or at least not needing a large amount of travel in other situations.

SUMMARY OF THE DISCLOSURE

[0006] In one aspect, there is provided an isolation device, which includes a hub, a pulley and at least one isolation spring arrangement. The hub is mountable to a shaft. The pulley is rotatably mounted to the hub. The at least one isolation spring arrangement includes a first isolation spring and a second isolation spring. Each of the first and second isolation springs is a helical compression spring having a length. The first isolation spring has a first spring rate. The second isolation has a second spring rate and is positioned in series with the first isolation spring. The first spring rate is higher than the second spring rate. The first and second isolation springs are arranged such that the first isolation spring transfers torque from the second isolation spring into a first one of the hub and the pulley and the second isolation spring transfers torque from the first isolation spring into a second one of the hub and the pulley. Initially during torque transfer from the first one of the hub and the pulley to the second one of the hub and the pulley, the entire first isolation spring is slid along a friction surface towards the second one of the hub and the pulley by the first one of the hub and the pulley during compression of the second isolation spring thereby generating a first frictional damping torque. Initially during torque transfer from the second one of the hub and the pulley to the first one of the hub and the pulley, at least a portion of the first isolation spring remains stationary relative to the friction surface and the entire second isolation spring is slid along the friction surface, during compression of the first isolation spring by the second one of the hub and the pulley, thereby generating a second frictional damping torque. The first and second spring rates and the lengths of the first and second isolation springs are selected such that the first frictional damping torque is greater than the second frictional damping torque. [0007] In another aspect, there is provided an isolation device, which includes a hub, a pulley and at least one isolation spring arrangement. The hub is mountable to a shaft. The pulley is rotatably mounted to the hub. The at least one isolation spring arrangement includes a first isolation spring and a second isolation spring. Each of the first and second isolation springs is a helical compression spring having a first end, a second end, and a plurality of coils between the first and second ends. The first ends of the first and second isolation springs face away from one another, and the second ends of the first and second isolation springs face one another. The first and second isolation springs each have a diameter, and extend along an arcuate path inside the pulley about an isolation device axis. The first isolation spring has a first spring rate, and wherein the second isolation has a second spring rate and is positioned in series with the first isolation spring, wherein the first spring rate is higher than the second spring rate. The first and second isolation springs are arranged such that the first isolation spring transfers torque from the second isolation spring into a first one of the hub and the pulley and the second isolation spring transfers torque from the first isolation spring into a second one of the hub and the pulley. A first spring drive surface on the first one of the hub and the pulley engages the first end of the first isolation spring, and a second spring drive surface on the second one of the hub and the pulley engages the first end of the second isolation spring. The second spring drive surface extends across a first portion of the diameter of the second isolation spring such that there is a space adjacent the second spring drive surface towards the isolation device axis. The space extends across a second portion of the diameter of the second isolation spring, from a side edge of the second spring drive surface to a radially inner edge of the second isolator spring relative to the isolation device axis. During torque transfer from the first one of the hub and the pulley to the second one of the hub and the pulley, the at least one isolation spring arrangement permits relative movement between the hub and the pulley through a first range of angular movement, and wherein, during torque transfer from the second one of the hub and the pulley to the first one of the hub and the pulley, the at least one isolation spring arrangement permits relative movement between the hub and the pulley through a second range of angular movement. The second spring rate and a size of the space are selected such that, at a selected torque transfer level during torque transfer between the hub and the pulley through the first and second isolation springs, the selected torque transfer level drives the coils of the second isolation spring to contact one another on the radially inner side of the second isolation spring relative to the isolation device axis, which in turn drives at least one of the coils at the free end of the second isolation spring to tip into the space, which in turn permits the first range of angular movement to exceed the second range of angular movement.

BRIEF DESCRIPTIONS OF THE DRAWINGS

[0008] For a better understanding of the embodiment(s) described herein and to show more clearly how the embodiment(s) may be carried into effect, reference will now be made, by way of example only, to the accompanying drawings in which:

[0009] Figure 1 is an elevation view of an engine with an isolation device in accordance with an embodiment of the present disclosure.

[0010] Figure 2 is a perspective view of the isolation device shown in Figure 1.

[0011] Figure 3 is a perspective exploded view of the isolation device shown in Figure 2.

[0012] Figure 4 is an isolation spring arrangement from a prior art isolation device.

[0013] Figure 5 is isolation spring arrangement from the isolation device shown in Figure

2.

[0014] Figure 6 is a perspective view of a portion of the isolation device shown in Figure 1 , showing torque transfer from a hub of the isolation device to a pulley of the isolation device.

[0015] Figure 7 is a perspective view of a portion of the isolation device shown in Figure 1 , showing torque transfer from a pulley of the isolation device to a hub of the isolation device.

[0016] Figure 8 is a graph illustrating torque output from the isolation device shown in Figure 1 on a test machine simulating an engine.

[0017] Figure 9 is a graph illustrating torque output from an isolation device of the prior art. [0018] Figure 10A is a plan view of the portion of the isolation device shown in Figure 6, showing a first range of movement available during torque transfer from the hub to the pulley.

[0019] Figure 10B is a plan view of the portion of the isolation device shown in Figure 7, showing a second range of movement available during torque transfer from the pulley to the hub.

[0020] Figure 1 1A is a magnified plan view of the isolation spring arrangement immediately prior to tipping of coils from one of the isolation springs in the isolation spring arrangement.

[0021] Figure 1 1 B is a magnified plan view of the isolation spring arrangement immediately after tipping of coils from one of the isolation springs in the isolation spring arrangement.

[0022] Figure 12 is a sectional view of a portion of the isolation device shown in Figure 2.

[0023] Figure 13 is a magnified view of one of the isolation springs in the isolation spring arrangement of the isolation device shown in Figure 2, with an optional flattening of certain surfaces thereof.

[0024] Figure 14 is a perspective view of a variant of the isolation device shown in Figure 2, where each isolation spring arrangement includes first, second and third isolation springs all in series with one another.

[0025] Figure 15 is a perspective view of another variant of the isolation device shown in Figure 2, where each isolation spring arrangement includes first, second and third isolation springs where two of the springs are in series and a third spring is in parallel with the two springs in series.

[0026] Figure 16 is a perspective view of yet another variant of the isolation device shown in Figure 2, including a connector that connects the isolation springs that make up the isolation spring arrangement. [0027] Unless otherwise specifically noted, articles depicted in the drawings are not necessarily drawn to scale.

DETAILED DESCRIPTION

[0028] For simplicity and clarity of illustration, where considered appropriate, reference numerals may be repeated among the Figures to indicate corresponding or analogous elements. In addition, numerous specific details are set forth in order to provide a thorough understanding of the embodiment or embodiments described herein. Flowever, it will be understood by those of ordinary skill in the art that the embodiments described herein may be practiced without these specific details. In other instances, well-known methods, procedures and components have not been described in detail so as not to obscure the embodiments described herein. It should be understood at the outset that, although exemplary embodiments are illustrated in the figures and described below, the principles of the present disclosure may be implemented using any number of techniques, whether currently known or not. The present disclosure should in no way be limited to the exemplary implementations and techniques illustrated in the drawings and described below.

[0029] Various terms used throughout the present description may be read and understood as follows, unless the context indicates otherwise:“or” as used throughout is inclusive, as though written“and/or”; singular articles and pronouns as used throughout include their plural forms, and vice versa; similarly, gendered pronouns include their counterpart pronouns so that pronouns should not be understood as limiting anything described herein to use, implementation, performance, etc. by a single gender;“exemplary” should be understood as“illustrative” or“exemplifying” and not necessarily as“preferred” over other embodiments. Further definitions for terms may be set out herein; these may apply to prior and subsequent instances of those terms, as will be understood from a reading of the present description. It will also be noted that the use of the term“a” will be understood to denote“at least one” in all instances unless explicitly stated otherwise or unless it would be understood to be obvious that it must mean“one”. [0030] Modifications, additions, or omissions may be made to the systems, apparatuses, and methods described herein without departing from the scope of the disclosure. For example, the components of the systems and apparatuses may be integrated or separated. Moreover, the operations of the systems and apparatuses disclosed herein may be performed by more, fewer, or other components and the methods described may include more, fewer, or other steps. Additionally, steps may be performed in any suitable order. As used in this document,“each” refers to each member of a set or each member of a subset of a set.

[0031] Reference is made to Figure 1 , which shows an engine 10 for a vehicle. The engine 10 includes a crankshaft 12 which drives an endless drive element, which may be, for example, a belt 14. Via the belt 14, the engine 10 drives a plurality of accessories 16 (shown in dashed outlines), such as a motor/generator unit (MGU) and an air conditioning compressor. Each accessory 16 includes an accessory shaft 15 with a pulley 13 thereon, which is driven by the belt 14. Additionally, shown in the present embodiment is an idler pulley shown at 17a on an idler shaft 17b, and a tensioner pulley 19a rotatably mounted on a tensioner arm 19b, which form part of a belt tensioner 19. The functions of the idler pulley 17a and the belt tensioner 19 are well known to one of skill in the art.

[0032] An isolation device 20 may be provided instead of a pulley, in one or more places to control torque transfer between the crankshaft 12 and the accessory shafts 15. In Figure 1 , the isolation device 20 is provided on the crankshaft 12. The isolation device 20 transfers torque between the crankshaft 12 and the belt 14, but attenuates torsional vibrations from the crankshaft 12 from being transmitted to the belt 14. Such torsional vibrations, oscillations in the speed of the crankshaft 12, are inherent to internal combustion piston engines. These oscillations are isolated from the belt 14 by the isolation device 20, and as a result, the stresses that would otherwise be incurred by the belt 14 and by the accessory shafts 15 are reduced.

[0033] Reference is made to Figures 2 and 3, which show a perspective assembled view, and a perspective exploded view of the isolation device 20, respectively. The isolation device 20 includes a hub 22, a pulley 24, first and isolation spring arrangements, each shown at 28. In the example shown in Figures 2 and 3, the isolation device 20 further includes optional elements including a bushing 29, seals 30 and a thrust plate 35.

[0034] The hub 22 includes a shaft adapter 22a and a driver 22b in the embodiment shown. The shaft adapter 22a is adapted to mount to the crankshaft 12 in any suitable way. For example, the shaft adapter 22 may have a shaft-mounting aperture 36 therethrough that defines a rotational axis A for the isolation device 20. The shaft mounting aperture 36 may be configured to snugly receive the end of the crankshaft 12. A plurality of shaft-mounting fasteners 37, such as bolts, (Figure 1 ) may be inserted through a distal end 38 shaft adapter 22a and driver 22b to fixedly mount them to the crankshaft 12 so that the hub 22 and the crankshaft 12 co-rotate together about the axis A.

[0035] The driver 22b includes first and second drive arms 100, individually shown at 100a and 100b. Each drive arm 100 has a first hub/spring interface surface 102 and a second hub/spring interface surface 104. The first and second hub/spring interface surfaces 102 and 104 are positioned to engage ends of the isolation spring arrangements 28 as described further below.

[0036] The pulley 24 is rotatably coupled to the shaft adapter 22. The pulley 24 has an outer surface which includes a belt engagement surface 40 that is configured to engage the belt 14 (Figure 1 ). The belt 14 may thus be a multiple-V belt.

[0037] The pulley 24 may be formed from a main pulley portion 24a that includes the belt engagement surface 40 thereon, and a pulley cover 24b that cooperates with the main pulley portion 24a to define a spring shell 42, for holding the first and second isolation spring arrangements 28.

[0038] The pulley 24 further includes an inner surface 43. The bushing 27 engages the inner surface 43 of the pulley 24 and rotatably supports the pulley 24 on the shaft adapter 22a. The bushing 27 may be a polymeric member that has a selected, low friction coefficient. Suitable materials for the bushing 27 include, for example, certain forms of nylon.

[0039] The pulley 24 includes two pairs of lugs that are formed by pressing in the material of the main pulley portion 24a and the pulley cover 24b inwardly. A first pair of lugs 109a is shown in Figure 3. The second pair of lugs 109b is shown in Figure 12. The first pair of lugs 109a face one another, and the second pair of lugs 109b face one another. The pulley 24 includes first and second pulley/spring interface surfaces 106 and 108, which are positioned to engage ends of the isolation spring arrangements 28, as described further below. In the embodiment shown, the first pulley/spring interface surfaces 106 are provided on a first side of the lugs 109a and 109b, and the second pulley/spring interface surfaces 108 are provided on a second side of the lugs 109a and 109b.

[0040] The isolation spring arrangements 28 are provided to accommodate oscillations in the speed of the crankshaft 12 in relation to the belt 14, as noted above. The isolation spring arrangements 28 may each include a first isolation spring 110 and a second isolation spring 112. Each of the first and second isolation springs 110 and 112 (Figure 5) is a helical compression spring, and preferably extends along an arcuate path inside the pulley 24. Each of the first and second isolation springs 110 and 112 has a first end 114, a second end 116, and a plurality of coils 118 between the first and second ends 114 and 116. The first ends 114 of the first and second isolation springs 110 and 112 face away from one another, and the second ends 116 of the first and second isolation springs 110 and 112 face one another. The first and second isolation springs 110 and 1 12 a length L1 and L2 (Figure 5), respectively, and a diameter D1 and D2 (Figure 5), respectively. The first and second isolation springs 110 and 112 have respective first and second spring rates K1 and K2. In the embodiment shown, the diameters D1 and D2 are approximately equal, though they do not need to be strictly equal. In the embodiment shown, the length L1 is greater than the length L2, though this need not be true in all embodiments. In the embodiment shown, the first spring rate K1 is greater than the second spring rate K2, though this need not be true in all embodiments.

[0041] The first and second isolation springs 1 10 and 112 are arranged in series with one another, such that the first isolation spring 1 10 transfers torque from the second isolation spring 112 into a first one of the hub 22 and the pulley 24 and the second isolation spring 112 transfers torque from the first isolation spring 110 into a second one of the hub 22 and the pulley 24. In the example shown in Figure 6, the first one of the hub 22 and the pulley 24 is the hub 22 and the second one of the hub 22 and the pulley 24 is the pulley 24. As can be seen in this example, the first end 114 of the second isolation spring 1 12 remains fixed rotationally relative to the pulley 24, while the driver 22b engages the first end 114 of the first isolation spring 110.

[0042] Because the first spring rate K1 is higher than the second spring rate K2, what occurs initially during torque transfer from the first one of the hub 22 and the pulley 24 to the second one of the hub 22 and the pulley 24, is that the entire first isolation spring 110 is slid along a friction surface 120 (which in this instance is a surface of the pulley cover 24b) towards the second one of the hub 22 and the pulley 24 by the first one of the hub 22 and the pulley 24 during compression of the second isolation spring 112 thereby generating a first frictional damping torque TF1. This damping torque can be seen in the torque/displacement curve shown at 200 in Figure 8. This damping torque TF1 arises from friction generated by the movement of the first isolation spring 110 along the friction surface 120, and by the movement of a portion of the second isolation spring 112 along the friction surface 120. Only a portion of the second isolation spring 112 moves, or moves significantly, along the friction surface 120 in this example, since the first end 114 of the second isolation spring 112 is engaged with the second pulley/spring interface surface 108.

[0043] During this initial range of torque transfer (shown at 202 in Figure 8), the effective spring rate of the isolation spring arrangement 28 is equal to 1/(1/K1 + 1/K2). Once the torque transfer through the first and second isolation springs 110 and 1 12 reaches a first selected torque transfer level TS1 (Figure 8), the first isolation spring 110 is fully compressed, at which point only the second isolation spring 112 continues to be compressed, which defines a second range of torque transfer. In this second period of torque transfer, the effective spring rate of the isolation spring arrangement 28 is only the spring rate K2, since the first spring is effectively a solid member, having been compressed fully. This second range of torque transfer is shown at 204 in Figure 8.

[0044] By contrast, Figure 7 (and the torque curve 250 in Figure 8) illustrate torque transfer from the second one of the hub 22 and the pulley 24 to the first one of the hub 22 and the pulley 24. As can be seen, the first end 114 of the second isolation spring 112 is engaged with the first pulley/spring interface surface 106. As a result, initially a portion of the second isolation spring 112 remains stationary relative to the friction surface 120 and the entire second isolation spring 112 is slid along the friction surface 120 during compression of the first isolation spring 110 by the second one of the hub 22 and the pulley 24, thereby generating a second frictional damping torque TF2 (Figure 8).

[0045] The first and second spring rates K1 and K2 and the lengths L1 and L2 of the first and second isolation springs 110 and 1 12 impact the first and second frictional damping torques TF1 and TF2, and may be selected such that the first frictional damping torque TF1 is greater than the second frictional damping torque TF2. The size of the difference between the first and second frictional damping torques TF1 and TF2 depends at least in part on such factors as the particular lengths selected for L1 and L2 and the particular spring rates selected for K1 and K2.

[0046] Also, in the example shown in Figure 7, relating to curve 250 in Figure 8, once the torque transfer through the first and second isolation springs 110 and 112 reaches a second selected torque transfer level TS2 (Figure 8), the first isolation spring 110 is again fully compressed, at which point only the second isolation spring 112 continues to be further compressed, which defines a second range of torque transfer. As can be seen, because of the increased amount of damping torque that is present initially during torque transfer from the first one of the hub 22 and the pulley 24 to the second one of the hub 22 and the pulley 24 relative to initially during transfer from the second one of the hub 22 and the pulley 24 to the first one of the hub 22 and the pulley 24, the first selected torque transfer level TS1 at which the first isolation spring 110 is fully compressed and the isolation spring arrangement 28 enters the second range of torque transfer is higher than the second selected torque transfer level TS2 at which the first isolation spring 110 is fully compressed and the isolation spring arrangement 28 enters the second range of torque transfer.

[0047] By contrast, an isolation spring arrangement of the prior art is shown at 280 in Figure 4 and has a torque curve that is shown at 300 in Figure 9. The torque curve 300 shown in Figure 9 is mathematically derived, and thus appears much cleaner than the torque curves shown in Figure 8, which were derived from a simulated engine. The isolation spring arrangement 280 shown in Figure 4 includes first and second isolation springs 282 and 284 which are nested (i.e. such that the second isolation spring 284 is nested within and is shorter than, the first isolation spring 282). With springs that are nested, the amount of frictional damping that is provided is more or less solely dependent on friction between the outer spring (i.e. the first isolation spring 282), and the friction surface (not shown) against which it rubs. Accordingly, there is essentially no difference in the amount of damping torque regardless of whether the hub of such an isolator would transfer torque to the pulley, or whether the pulley would transfer torque to the hub. Thus the curve 300 is representative of the torque transfer both ways, (i.e. regardless of which end of the isolation spring assembly 280 is being moving relative to the friction surface against which the isolation spring arrangement 280 slides).

[0048] These properties of the isolation device 20 described herein, may be advantageous in a number of situations or applications. For example, in a situation in which the engine 10 is equipped with the MGU 16a, the engine 10 may have two modes of starting, including a first start mode (referred to as a key start) in which the engine 10 is started via a starter motor engaged with the flywheel until combustion takes over, and a second start mode (referred to as an MGU start) in which the MGU drives the crankshaft 12 via the belt 14 until combustion takes over. During a key start, it may be desirable to have a relatively high amount of friction in the initial range of torque transfer through the isolation device 20, and it may be desirable to move the torque at which the isolation spring arrangement 28 enters the second range of torque transfer to be as late as possible. This inhibits the isolation device 20 from cycling between the first ranges and second ranges of torque transfer. During an MGU start, however, there may be less need for frictional damping for certain reasons. For example, during an MGU start there is a lower likelihood of resonance from occurring.

[0049] Another feature of the isolation device 20 is illustrated in Figures 11 and 12, and relates to the hub/spring interface surfaces 102 and 104 and in particular the pulley/spring interface surfaces 106 and 108. For the purposes of discussing this feature, whichever of the hub/spring interface surfaces 102 and 104 or the pulley/spring interface surfaces 106 and 108 is engaged with the first end 114 of the first isolation spring 110 will be referred to as a first spring drive surface 140, and whichever of the hub/spring interface surfaces 102 and 104 or the pulley/spring interface surfaces 106 and 108 is engaged with the first end 114 of the second isolation spring 112 will be referred to as a second spring drive surface 142. In the example situation shown in Figure 6, the first spring drive surfaces 140 are the first hub/spring interface surfaces 104, and the second spring drive surfaces 142 are the first pulley/spring interface surfaces 106.

[0050] As can be seen based on Figures 6 and 12, the second spring drive surface 142 extends across a first portion 144 of the diameter D2 of the second isolation spring 112 such that there is a space 146 adjacent the second spring drive surface 142 towards the isolation device axis A. The space 146 extends across a second portion 148 of the diameter D2 of the second isolation spring 1 12, from a side edge of the second spring drive surface 142 to a radially inner side 150 of the second isolator spring 112 relative to the isolation device axis A.

[0051] As can be seen from Figures 10A and 10B, during torque transfer from the first one of the hub 22 and the pulley 24 to the second one of the hub 22 and the pulley 24, the isolation spring arrangements 28 permit relative movement between the hub 22 and the pulley 24 through a first range of angular movement (R1 shown in Figure 10A), and wherein, during torque transfer from the second one of the hub 22 and the pulley 24 to the first one of the hub 22 and the pulley 24, the isolation spring arrangements permit relative movement between the hub 22 and the pulley 24 through a second range of angular movement R2 shown in Figure 10B.

[0052] The second spring rate K2 and the size of the space 146 are selected such that, at a selected torque transfer level TS3 during torque transfer between the hub 22 and the pulley 24 through the first and second isolation springs 1 10 and 112, the selected torque transfer level TS3 drives the coils 118 of the second isolation spring 112 to contact one another on the radially inner side 150 of the second isolation spring 1 12 relative to the isolation device axis A, and to drive at least one of the coils 1 18 at the first end 114 of the second isolation spring 112 to tip into the space 146, which in turn permits the first range of angular movement to exceed the second range of angular movement.

[0053] The reason for this is that the first spring rate K1 of the first isolation spring 110 is relatively high. As a result, there is no tendency for the first isolation spring 110 to tip into the space 146 in order to extend the range of movement available, when the first spring drive surface 140 is one of the pulley/spring interface surfaces 106 and 108. This extension of the first range of movement relative to the second range of movement is advantageous in certain scenarios. For example, when the engine undergoes a key start, it is beneficial to provide as much range of movement as possible in order to prevent lock up of the isolation device 20. However, by contrast, during an MGU start, it is sometimes considered advantageous to have a shorter range of movement prior to lock up of the isolation device, in order to provide high torque to the crankshaft 12 relatively quickly.

[0054] The space 146 may extend across any suitable amount of the diameter of the second isolation spring 112. In an embodiment, the space 146 may extend across at least 30% of the diameter of the second isolation spring 112. In an embodiment, the space 146 may extend across at least one third of the diameter of the second isolation spring 1 12.

[0055] It will be noted that the first and second isolation springs shown in the embodiment shown in Figures 3-12 are coiled oppositely to one another. As a result, when torque is transferred through their respective second ends 116 to one another, there is no likelihood of the first and second isolation springs 110 and 112 entangling. By contrast, this would be possible if the first and second isolation springs 1 10 and 112 were coiled the same way (e.g. both right handed, or left handed coiling).

[0056] Reference is made to Figure 13, which shows an optional feature on the second isolation spring 112. In order to reduce stresses on the coils 118 and slippage between the coils 118 of the isolation spring 112 when the torque applied through the isolation spring arrangement 28 is such that the coils 118 of the second isolation spring 112 contact one another, the mating surfaces shown at 180 of the coils 1 18 (i.e. also referred to as the intra coil surfaces 180, are flattened prior to formation of the stock wire into the second isolation spring 112.

[0057] Reference is made to Figure 14, which shows a variant of the isolation device 20, in which each isolation spring arrangement 28 includes the first isolation spring 110, the second isolation spring 112 and a third isolation spring 182 that is in series with the first and second isolation springs 110 and 1 12. In the embodiment shown, the third isolation spring 182 has a third spring rate K3 that is higher than the second spring rate K2, and which may be higher or lower than the first spring rate K1. The advantages above regarding the increased amount of damping torque, the shift in the torque at which the isolation device enters into the second range of torque transfer and the increased range of movement during torque transfer are all present in this variant.

[0058] Reference is made to Figure 15, which shows another variant of the isolation device 20, in which each isolation spring arrangement 28 includes the first isolation spring 110, the second isolation spring 112 and a third isolation spring 186 that is in parallel with the first and second isolation springs 110 and 112. In the embodiment shown, the third isolation spring 182 has a third spring rate K3 that is higher than the second spring rate K2, and which may be higher or lower than the first spring rate K1. The advantages above regarding the increased amount of damping torque, the shift in the torque at which the isolation device enters into the second range of torque transfer and the increased range of movement during torque transfer are all present in this variant.

[0059] A variant of the isolation device 20 is shown in Figure 16. As can be seen, a connector 190 is provided, which holds the second ends 116 of the first and second isolation springs 110 and 112. The connector includes a plate 192 that engages the second ends 116 of the first and second isolation springs 110 and 112, a first projection 194 extending from the plate 192 into the first isolation spring 110 (i.e. into a hollow 195 in the first isolation spring 110), and a second projection 196 extending from the plate 192 into the second isolation spring 1 12 (i.e. into a hollow 197 in the second isolation spring 112. The plate 192 and projections 194 and 196 maintain the second ends 116 of the first and second isolation springs 1 10 and 112 parallel with one another, so as to maintain torque transfer across an entirety of the second ends 1 16 between the first and second isolation springs 110 and 112.

[0060] It will be noted that, while the embodiments herein show the isolation device 20 on the crankshaft 12 it is alternatively possible to provide the isolation device 20 on the shaft of the MGU 16a or any other suitable accessory. In such embodiments, the arrangement of the first and second isolation springs 110 and 112 may need to be reversed, depending on when the application calls for higher friction, longer travel and any of the other features described herein.

[0061] Persons skilled in the art will appreciate that there are yet more alternative implementations and modifications possible, and that the above examples are only illustrations of one or more implementations. The scope, therefore, is only to be limited by the claims appended hereto and any amendments made thereto.