The present invention relates to a tool system for mounting an elastic sleeve and to a corresponding method for mounting an elastic sleeve.

When mounting cable connections or terminations e. g. in the field of medium voltage cabling, elastic sleeves (also called cold shrink sleeves in the following) are used for covering the electrically conductive parts of the connection or termination.

For supporting the elastic sleeve from the inside in a stretched condition during and before mounting it over the connection and/or termination, it is for instance known to use a hollow support tube formed by a plastic spiral that can be removed when the elastic sleeve has to contract. However, such spiral support tubes are expensive and cause a lot of waste. The mounting procedure of spiral tubes is in many cases more time consuming and bears the risk of damaging the cable or pre-installed mastics.

Further, it is known to hold the elastic sleeve on an outer holdout tube which is attached to the outer surface of the sleeve in order to keep it in the expanded state. Such outer holdouts have to be destroyed or removed for allowing the elastic sleeve to contract. Also this kind of holdout tubes produces a lot of waste and the expanded assembly is challenging to produce. Another option are holdouts that have a supporting tube which is covered with a pressure resistant grease. For mounting the elastic sleeve slides on the grease.

There is still a need for an improved tool system overcoming at least some of the problems with known holdout systems, the tool system allowing an efficient assembly of an elastic sleeve, further having a high degree of safety during use, at the same time being robust and economic to manufacture. Preferably, at least a part of the involved components should be re-usable.

This object is solved by the subject matter of the independent claims. Advantageous embodiments of the present invention are the subject matter of the dependent claims. The present invention is based on the idea that an elastic sleeve can be assembled over a connection or termination if it is expanded over a rigid holdout tube, being brought into position around the connection or termination, and is pushed off the holdout tube in an axial direction. By applying an axial pressure which is evenly distributed around the circumference of the end face of the elastic sleeve, a smooth and uniform gliding movement of the sleeve with respect to the holdout tube can be achieved. The sleeve may slide in direct contact with the tube or the tube may be covered with significant amounts of (pressure resistant) grease in the interface and/or a film with or without surface coatings such as silicone is arranged in the interface between the tube and the sleeve. Moreover, employing the lever principle allows an operatorto introduce sufficiently high forces to overcome the friction between the expanded elastic sleeve and the holdout tube without applying extremely high manual forces which are unacceptable to some customers or may cause deformation of the cable.

In particular, the present invention provides a tool system for mounting an elastic sleeve, the tool system comprising a holdout tube for supporting the elastic sleeve prior to and during mounting, the holdout tube having a longitudinal axis, an interface element which is moveable along the longitudinal axis for transferring pressure onto the elastic sleeve in order to push it off the holdout tube during mounting, and an actuation lever, which engages with the holdout tube at a fulcrum region of the lever. The actuation lever comprises two load arms for partly encompassing the holdout tube, wherein load regions are arranged at a peripheral end of each of the load arms, and wherein the actuation lever is operable to actuate the interface element by pressing the load regions of the actuation lever against the interface element.

In other words, the actuation lever forms a so-called class 1 lever, where the fulcrum is placed between the effort and the load. The movement of the load (here: the pushing of the interface element) is in the opposite direction of the movement of the effort (here: the pushing of an operator mounting the elastic sleeve). In order to achieve an amplification of the force, the load arm, i. e. the distance between the fulcrum and the contact to the interface element, is shorter than the effort arm, i. e. the distance between the fulcrum and the point of contact of the operator.

Advantageously, the interface element transforms the essentially punctiform pressure exerted by the actuation lever into an evenly distributed pressure that acts around the circumference of the end face of the elastic sleeve. When the sleeve is coming free from the holdout tube at its end opposite to the end face that is in contact with the interface element, the sleeve shrinks and contracts around the component to be covered. It has to be noted that after the gliding movement of the elastic sleeve has been initiated, the friction forces become lower, so that the pressure exerted by the actuation lever does not have to be upheld for the complete distance until the holdout tube is fully removed. It is often sufficient for the highest pressure to act on the elastic sleeve while the sleeve is moved to the end of the holdout tube and to about 5 % of the total length of the sleeve off the holdout tube. After that distance, the contracting sleeve itself starts pushing the holdout tube from the other side, thus assisting the operation of the actuation lever or preferably making further operation of the lever obsolete by creating a self-mounting process.

According to an advantageous embodiment of the present invention, each load region is arranged at the load arm to engage with the interface element at an equatorial position of the holdout tube. In other words, the points where the load regions engage with the interface element are located about 90° offset from the fulcrum region in a radial direction, the contact points being connected by an imaginary line leading through the center of the cross-section of the holdout tube and the load arms having the same length. Thus, the force exerted by the actuation lever acts on the interface element in a symmetrical manner, thus mostly avoiding any tilting and jamming of the interface element and reducing risk of damage to the holdout tube and/or film or grease layer. Further, it reduces the overall push force as the ring creates much less friction forces on the tube.

Advantageously, the actuation lever may be formed as a cam lever, in other words, each load region comprises a curved outline for keeping the actuation lever in contact with the interface element at an essentially constant contact point during the swiveling motion. This allows that the point of contact between the actuation lever and the interface element essentially remains at the same equatorial position during the swiveling movement of the actuation lever. Thus, the actuation lever always acts on the interface element in a symmetrical manner, thus avoiding any tilting and jamming of the interface element. Of course, the actuation lever may also sometimes not be in contact with the interface element during the course of the mounting process.

According to a further advantageous embodiment, the actuation lever has a lever axis and comprises at least one pin arranged in the fulcrum region, wherein the pin extends in a direction along the lever axis and is operable to engage with at least one matching opening provided at the outer circumference of the holdout tube. Such a pin and opening construction has the advantage that it can be produced economically and that the operator can attach the actuation lever to the holdout tube in an easy manner.

For providing a more secure attachment of the actuation lever to the holdout tube, the actuation lever may comprise at least one hook element arranged in the fulcrum region, wherein the hook element is operable to engage with at least one matching recess provided at the outer circumference of the holdout tube.

Providing openings or recesses at the holdout tube has the advantage that the holdout tube has an essentially smooth outer surface without any protrusions projecting from the holdout tube. However, for a firmer grip between the actuation lever and the holdout tube, the actuation lever may also comprise at least one pivot spindle arranged in the fulcrum region, wherein the pivot spindle is operable to engage with at least one matching bearing element provided at the outer circumference of the holdout tube. In this case, the bearing element may advantageously comprise a hook-shaped protrusion which engages with the spindle. The pivot spindle may also be simply a part of a wire loop arranged at the actuation lever or it may be integral with the lever.

Advantageously, the interface element comprises a slidable tube with an inner diameter that is larger than the outer diameter of the holdout tube, wherein the slidable tube has a first end face which in operation comes into abutting contact with an end face of the elastic sleeve, and a second end face which in operation is in contact with the load regions of the actuation lever. Such a preferably cylindrical tube can be fabricated economically and can efficiently provide the preferably uniformly distributed axial pressure. In order to further strengthen the interface element, the slidable tube may have a ring-shaped force distribution flange at one or both of the first and second end faces. The interface element may for instance be fabricated from a rigid plastic material such as polypropylene (PP), polystyrene (PS), or may be made at least partly from metal. Advantageously, the interface element is re-usable and/or it has design features to ease removal such as openable interlocks or recesses which are easy to cut with standard tools. In order to provide a cost-effective and robust tool system, the actuation lever is advantageously formed as one single-piece part. The actuation lever may be formed from a rigid plastic material such as polyamide (PA) or may at least partly be made from metal.

The present invention further relates to a method for mounting an elastic sleeve, the method comprising the following steps: providing a holdout tube for supporting the elastic sleeve prior to and during mounting, the holdout tube having a longitudinal axis, and attaching the elastic sleeve in an expanded state around the holdout tube; mounting an interface element which encompasses the holdout tube at least partly and which is moveable along the longitudinal axis; providing an actuation lever and engaging the actuation lever with the holdout tube at a fulcrum region of the lever, wherein the actuation lever comprises two load arms for partly encompassing the holdout tube, wherein load regions are arranged at a peripheral end of each of the load arms; pivoting the actuation lever to actuate the interface element by pressing the load regions of the actuation lever against the interface element, wherein the interface element is moved by the actuation of the lever along the longitudinal axis, so that the interface element transfers pressure onto the elastic sleeve in order to push it off the holdout tube.

It has to be noted that the individual steps and parts thereof may be performed in any suitable sequence. For instance, the interface element may be mounted before the elastic sleeve is mounted around the holdout tube.

According to an advantageous example of the present disclosure, each load region is arranged at the load arm to engage with the interface element at an equatorial position of the cross-section. This allows for a symmetric force transfer, so that the interface element does not tilt and get blocked in its movement. In particular, each load region may comprise a curved outline which during the swiveling of the actuation lever remains in contact with the interface element at an essentially constant contact point. In other words, the load region of the actuation lever acts as a cam, thus ensuring a smooth movement of the interface element and a uniform force transmission to the elastic sleeve.

The fulcrum region where the actuation lever interacts with the holdout tube may have various different geometries. Thus, the step of engaging the actuation lever at the fulcrum region may comprise engaging at least one pin, which extends in a direction along the lever axis, with at least one matching opening provided at the outer circumference of the holdout tube, or engaging at least one hook element arranged in the fulcrum region with at least one matching recess provided at the outer circumference of the holdout tube, or engaging at least one pivot spindle arranged in the fulcrum region with at least one matching bearing element provided at the outer circumference of the holdout tube.

As mentioned above, the high forces exerted by the actuation lever are not necessarily needed for moving the elastic sleeve off the holdout tube along the complete length of the sleeve. However, in order to extend this distance further, the step of engaging the actuation lever at the fulcrum region is repeated at least once after the interface element has been pushed a predetermined distance. This repetition can be achieved by providing redundant anchoring means arranged sequentially in an axial direction along the holdout tube. The nature and geometry of the anchoring means depends on the particular structure of the fulcrum means arranged at the fulcrum region of the actuation lever. Fora fulcrum means comprising one or more pins, a series of two or more openings or a slotted notch may be arranged at the holdout tube to receive the pin. If the fulcrum means comprise a pivot spindle, a series of corresponding bearing means may be provided as the anchoring means at the holdout tube.

In most applications, when having openings in the tube, it is a requirement that the elastic sleeve must not be positioned over these openings. Thus, the design of the interface element and the actuation lever must be executed such that the elastic sleeve is positioned beyond the last opening. One option to achieve this is to use an interface element with a high width and/or an actuation lever with wide and/or long load arms. According design features are employed when having anchoring elements. In this case, interface elements may be slotted to be positioned at least partly in the region of the anchoring elements. The accompanying drawings are incorporated into the specification and form a part of the specification to illustrate several embodiments of the present invention. These drawings, together with the description serve to explain the principles of the invention. The drawings are merely for the purpose of illustrating the preferred and alternative examples of how the invention can be made and used, and are not to be construed as limiting the invention to only the illustrated and described embodiments. Furthermore, several aspects of the embodiments may form — individually or in different combinations — solutions according to the present invention. The following described embodiments thus can be considered either alone or in an arbitrary combination thereof. Further features and advantages will become apparent from the following more particular description of the various embodiments of the invention, as illustrated in the accompanying drawings, in which like references refer to like elements, and wherein:

FIG. 1-3 show a schematic side view of a tool system according to a first example in three different operational states;

FIG. 4 is a schematic perspective view of an actuation lever according to a first example;

FIG. 5 is a rotated schematic perspective view of the actuation lever shown in Fig. 4;

FIG. 6 is a schematic side view of a holdout tube according to a first example;

FIG. 7 is a schematic perspective view of the holdout tube of Fig. 6;

FIG. 8 is a schematic side view of a holdout tube according to a second example;

FIG. 9 is a schematic perspective view of the holdout tube of Fig. 8;

FIG. 10 is a schematic perspective view of a part of a holdout tube according to a further example;

FIG. 11 is a rotated schematic perspective view of the holdout tube shown in Fig. 10;

FIG. 12 is another rotated schematic perspective view of the holdout tube shown in Fig. 10;

FIG. 13 is a schematic perspective view of an actuation lever according to another example;

FIG. 14 is a rotated schematic perspective view of the actuation lever shown in Fig. 13;

FIG. 15 is a schematic perspective view of an actuation lever according to another example being engaged with a matching holdout tube; FIG. 16 is a schematic perspective view of a part of a holdout tube according to a further example;

FIG. 17 is a schematic side view of the holdout tube shown in Fig. 16;

FIG. 18 is a schematic cross-sectional view of a part of a holdout tube according to a further example, with an interface element mounted thereon;

FIG. 19 is a schematic side view of the holdout tube and interface element shown in Fig. 18;

FIG. 20 is a schematic perspective view of an actuation lever according to another example;

FIG. 21 is a rotated schematic perspective view of the actuation lever shown in Fig. 20;

FIG. 22 shows a schematic perspective view of a tool system according to a further example;

FIG. 23 shows another schematic perspective view of the tool system according to Fig. 22;

FIG. 24 shows another schematic perspective view of the tool system according to Fig. 22.

The present invention will now be explained in more detail with reference to the Figures and firstly referring to Fig. 1 to 3.

Fig. 1 to 3 show a schematic perspective side view of a tool system 100 in three different operational stages in order to explain the working principle of the present invention. It has to be noted that the elastic sleeve is not shown in these drawings. Further, it should be noted that all the drawings in the present Figures are not drawn to scale and that the proportions and dimensions may in reality be different and may be chosen as needed.

The tool system 100 for mounting an elastic sleeve comprises a cylindrical holdout tube 102 made from a rigid plastic material on which the elastic sleeve (not shown in these Figures) can be mounted in an expanded state. Although not shown in the Figures, the same design features and principles apply when having a slidable film and/or grease positioned between holdout tube and elastic sleeve. The tool system 100 further comprises an actuation lever 104, which engages with the holdout tube 102 in a fulcrum region 106. As this is known for a class 1 lever, the fulcrum region 106 is located between a load region 108 that actuates the load, and an effort region 110 on which the operator exerts a force. As this will become more apparent from Fig. 4, the load region 108 comprises two arms encompassing the holdout tube 102.

In order to amplify the force exerted by the operator (symbolized by the arrow 112), a load arm 114 is shorter than an effort arm 116. When pressing the effort region 110 in the direction indicated by arrow 112, the load region 108 moves in the opposite direction. A transfer ratio of the effort force to the load force may for instance be 1:4.

According to the present invention, the tool system 100 further comprises an interface element 118 which comes into contact with the elastic sleeve. When the actuation element 104 is swiveled around the fulcrum region 106, the interface element is pressed in the direction indicated by arrow 120.

Each of the two arms of the load region 108 comprises a convex curved cam element 122. The cam element 122 for instance has an essentially circular outline, so that a point of contact between the cam element 122 and the end face 124 of the interface element 118 remains close to a central longitudinal axis of the holdout tube 102. Consequently, the contact points remain essentially at equatorial positions of the cross-section of the interface element 118 and the forces exerted at the contact points act on the interface element 118 in an essentially symmetric manner (with respect to the longitudinal center axis of the holdout tube 102), so that the interface element 118 is not tilted and will not be blocked in its movement along the holdout tube 118.

The pushing operation illustrated in Fig. 1 to 3 starts with the actuation lever 104 being tilted towards the interface element 118 at a starting angle of about 70° with respect to the longitudinal axis of the holdout tube 102. By pressing the actuation lever 104 in a direction indicated by the arrows 112, an upright position of the actuation lever (90° with respect to the longitudinal axis of the holdout tube 102, see Fig. 2) is passed and a final angle of about 120° with respect to the longitudinal axis of the holdout tube 102 is reached. Due to this swiveling motion, the interface element 118 is pushed axially along the holdout tube 102 in the direction of arrow 120. The second end face 126 of the interface element 118 in use is in abutting contact with an end face of the elastic sleeve (not shown in Fig. 1 to 3) and pushes the sleeve in a direction along arrow 120 off the holdout tube 102.

Fig. 4 and Fig 5 show two perspective views of an actuation lever 104 according to a first example. The actuation lever 104 may for instance be manufactured from a rigid plastic material that is stiff enough to withstand the occurring bending forces. Of course, the actuation lever 104 can also be fabricated as a whole or partly from metal, such as aluminum or steel. The pins 128 may also be fabricated integrally with the actuation lever 104, using a stable material for the lever, such as polyamide (PA) or glass filled polypropylene (PP-GF). The holdout tube 102 is typically molded from polypropylene (PP).

According to a first example, the actuation lever 104 comprises as fulcrum means two pins 128 which are formed to engage in belonging openings at the holdout tube 102. In the shown example, the pins are metal bolts extending in a direction along a longitudinal axis of the actuation lever 104. It is also clear that more pins or only one pin may also be provided according to the present invention. The cross-section of the pins 128 may be round or oval or any other suitable shape.

The pins 130 are overmolded by a plastic material forming the rest of the actuation lever 104. In order to provide sufficient mechanical stability, the actuation lever 104 comprises reinforcement ribs 132 at various particularly strained portions. As there are high forces acting on the pins, the option of choosing metal allows to reduce their overall size. The mating openings of the holdout tube, which is typically made from polypropylene (PP), have essentially the same dimensions, but plastic deformation is acceptable as the openings are used only for one or parts of one mounting process, whereas the actual lever may be re-used several times. For facilitating the operation by an operator, the actuation lever 104 has a handle 130 arranged in the effort region 110.

Fig. 6 and 7 illustrate a cylindrical holdout tube 102 according to a first example that can be combined with the actuation lever 104 of Fig. 4 and 5. According to this example, the holdout tube 102 has a pair of openings which match in their outline to the outline of the two pins 130. In the present case, the openings 134 have the shape of circular bores. It is clear for a person skilled in the art that the openings 134 may also have any other shape suitable to function as anchor points for the pins 130. In the shown example, the number of openings 134 corresponds to the number of pins. This is of course not mandatory. Instead, also only one elongated opening may be provided along the circumference of the holdout tube 102. The diameter and/or shape of the openings and/or the pins may be chosen to increase the tiling angle i.e. by having larger openings than pins or adding significant chamfers on the inside and/or outside of the openings.

Fig. 8 and 9 illustrate a cylindrical holdout tube 102’ according to another example that can be combined with the actuation lever 104 of Fig. 4 and 5. With only one set of openings 134 (as shown in Fig. 7 and 7), only one stroke of the swiveling operation of the actuation lever 104 can be performed. However, the pushing distance that can be achieved thereby may not be enough. Consequently, one or more additional sets of openings 134 may be arranged along the longitudinal axis of the holdout tube 102’. The operator can therefore take the actuation lever 104 out of the first set of openings 134 after having performed a first swiveling motion and insert the actuation lever 104 into the adjacent set of openings 134’. Of course, even more than one additional set of openings 134’ may also be provided.

Furthermore, as illustrated with the partial perspective views of Figures 10 to 12, instead of separate sets of openings 134, 134’ according to a further example, the holdout tube 102” comprises two slotted notches 136 which function as a gate for stepwise changing the position of the fulcrum region in an axial direction. The advantage of using slotted notches 136 instead of individual openings is that the actuation lever 104 does not have to be removed completely and then re-inserted into a small opening, but has just to be shifted in a radial direction and then be pushed into the next following slot 138 by moving it first in an axial and then in a radial direction, similar to the principle of a gear shift. After the actuation lever is fixed again in the next slot 138, the swiveling motion shown in Fig. 1 to 3 can be repeated. As shown with the example of Fig. 10 to 12, the actuation lever 104 can take four consecutive positions. Of course, also a longer notch

136 having more than four slots 138 can also be provided.

As shown in Figures 13 and 14, according to a further advantageous example of the present disclosure, the fulcrum means at the actuation lever 104’ may also comprise a hook shaped fulcrum means 140 instead of the pins 128. The hook shaped fulcrum means 140 may engage into an elongated opening provided in the holdout tube (not shown in the Figures). As compared to the example using straight pins, the hook shaped fulcrum means 140 have the advantage that the actuation lever 104’ can be swiveled around a larger angle. The hook shaped fulcrum means 140 may be fabricated as an integral part of the actuation lever or may be formed from a different material embedded into the material forming the rest of the actuation lever. The hook shaped fulcrum means 140 may be also be made from the same material but may be manufactured as a separate piece which is assembled on site or already in the manufacturing facility.

Figure 15 illustrates a further advantageous example of a holdout tube 202 and an actuation lever 204, the interface element not being shown in this Figure. The functioning of the entire tool system is the same as described above with the exception that the fulcrum region 206 is designed differently. In particular, the actuation lever 204 has a pivot spindle 242 which is held rotatably in a matching bearing element 244 arranged at the outer surface of the holdout tube 202.

An advantage of the construction shown in Fig. 15 can be seen in the fact that the actuation lever can be rotated around the axis defined by the pivot spindle 242 by a significantly larger swivel angle as compared for instance with the design using pins (see Fig. 4 and 5). Further, the pivot spindle 242 can be fixed very stably at the actuation lever 204 for instance by means of screw nuts 246. For instance, the pivot spindle 242 may be fabricated from metal, such as steel. Moreover, the transmission of the force is more symmetrical than when using two pins as the fulcrum means.

As can be seen from Fig. 15 together with Figures 16 and 17, also more than one bearing element 244 can be provided, the second bearing element 244 being off-set in an axial direction, so that the pushing distance for mounting the elastic sleeve can be extended. When mounting the sleeve, the actuation lever 204 is first engaged with the most peripheral bearing element 244. Then, the swiveling motion of the actuation lever 204 is performed, pushing the sleeve via the interface

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PATENT- UND RECHTSANWALTE element. Next, the actuation lever is disengaged from the most peripheral bearing element 244 and engaged with the next following bearing element 244’. Then, the swiveling motion of the actuation lever 204 is performed again, pushing the sleeve further via the interface element. Of course, also more or less than the shown two bearing elements can be provided. However, the distance that can be covered by these two bearing elements has turned out to be particularly efficient.

Fig. 18 and 19 schematically illustrate an embodiment with three bearing elements 344 arranged at the holdout tube 302. Moreover, in these drawings also the interface element 318 and the elastic sleeve 348 are depicted schematically. Advantageously, the interface element 318 is formed as a cylindrical slidable tube (also called push ring) with an inner diameter that is larger than the outer diameter of the holdout tube 302, wherein the slidable tube 318 has a first end face 326 which in operation comes into abutting contact with an end face of the elastic sleeve 348, and a second end face 324 which in operation is in contact with the load regions of the actuation lever. For reinforcing the interface element 318, the slidable tube has a ring-shaped force distribution flange 350, 351 at one or both of the first and second end faces 324, 326, respectively. Thus, the mechanical contact area between the interface element 318 and the sleeve 348 is enlarged, so that a particularly uniform force transmission can be achieved for smoothly moving the elastic sleeve 348 off the holdout tube 302 along the longitudinal axis 352. In Fig. 20 and 21 a schematic depiction of an actuation lever 304 according to a further example is shown. The actuation lever 304 may for instance be used together with the hook-shaped bearing elements 344 of Fig. 18 and 19. The actuation lever 304 is essentially identical to the actuation lever 104 and 204 shown above, with the exception that the fulcrum element is formed as a wire loop 354 which could also be formed as an essentially straight bolt. Figures 22 to 24 show a schematic perspective view of a tool system 400 according to a further example of the present disclosure.

In particular, in Fig. 22, 23 and 24 a schematic depiction of an actuation lever 404 according to a further example is shown. The actuation lever 404 does not comprise a bearing element. In this design, a bearing element 444 is formed integral with the holdout tube 402. The bearing element 444 may for instance comprise a cylindrical bolt 445 which extends across to the longitudinal axis of the actuation lever 404 and across to the longitudinal axis of the holdout tube 402. As shown in Figures 22 to 24, the bolt 445 is clipped in a hook-shaped support element

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PATENT- UND RECHTSANWALTE 468 provided at the holdout tube 402. In order to provide a higher flexibility for the operator mounting the elastic sleeve, more than one such support element 468 may be arranged at the holdout tube 402 for changing the position of the bolt 445. As shown here, two support elements

468 are arranged on opposing sides of the holdout tube 402. According to the example shown in Figures 22 to 24, the actuation lever 404 has an essentially U-shaped form with a base 464 and two free-cut arms 466 extending from the base 464. During the actuation move of the actuation lever 404, the bearing element 444 moves relative to the actuation lever 404 in a translational direction, whereas the lever moves only in a rotational move relative to the interface element 418. In other words, according to this example, the position of the fulcrum region moves during the actuation, thereby changing the ratio between the lengths of the load arm to the effort arm. The more the actuation lever 404 is swiveled from the upright position, the shorter gets the effort arm compared to the load arm. This means that the leverage is highest at the beginning of the swiveling motion. The bearing element 444 may engage with a notch 456 arranged on the backside of each arm of the actuation lever 404 as this is shown in Figures 22 and 23. According to an alternative example, the peripheral ends of the bearing element 444 may be positioned inside a slot 458 on each load arm 414 of the actuation lever 404 as shown in Figure 24.

The actuation lever 404 may have advantageously a protrusion 460 that points towards the holdout tube 402 and engages with a cavity 462 provided at the interface element 418. The protrusion 460 can be rotated in the cavity 462 when the actuation lever 404 is tilted. As shown in Figure 22, the actuation lever 404 and the interface element 418 are mounted together before the mounting of the elastic sleeve commences.

As shown in Figures 22 to 24, the holdout tube 402 comprises two half-shells separated in a radial direction in order to facilitate removing it after mounting. Such a multipart design may of course be used with the previously explained designs as well. Moreover, the holdout tube 402 may also comprise more than one section forming the cylindrical tube shape. Further, the holdout tube 404 may also be comprises several parts which are separated in an axial direction.

In order to reduce the friction between the outer surface 470 of the holdout tube 402 and the elastic sleeve, the outer surface of the holdout tube 402 may be provided with rounded, flat, dome shaped microstructures that provide a roughening of the surface. Such microstructures may for instance be fabricated by laser-structuring or etching the mold with which the holdout tube 402 is manufactured. Further, a film or foil or a layer of grease may be arranged between holdout tube 402 and the elastic sleeve in order to reduce the friction between the two components. When

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PATENT- UND RECHTSANWALTE using a film, it is particularly important that there is no mechanical contact between the actuation lever 404 and the outer surface 470 of the holdout tube 402 in order to avoid damaging the film.

Again, such friction reducing measures are applicable to all examples of the present disclosure.

In summary, the present invention relates to elastic sleeves which are mounted by sliding it from a rigid holdout tube. The tool system also includes a lever to initiate the self-mounting of the elastomeric part which is pre-expanded onto the holdout This means, the lever has to be able to generate the forces required to overcome the static friction of the elastic sleeve and to move it a certain distance along the holdout tube. The push length must be large enough to allow at least parts of the joint body to start recover as it is pushed beyond the end of the holdout tube. This requires high forces and a mechanism that allows for such pushing lengths.

For instance, the lever of the pin-type concept has at least one protrusion that is engaging with the holdout tube. Preferably, a pair of pins is used. The cross-section of the pins may be round or it may be oval or have any other shape that generates sufficient contact area with the holdout tube. The pins may be made from metal or be integral with the lever by using a more stable material for the lever, e. g. PA or PP-GF. The holdout tube is typically molded from PP.

The zone where the pins are engaging with the holdout tube are the pivot point of the rotational move of the lever (see Fig. 1 to 3). At the top the jointer applies a majorly axial force of up to 150 N. Through the pivot point this force is being transformed into an axial push force at the lower end directed into the opposite direction. This force may be higher than the force applied at the top depending on design features (relative length of upper and lower part of the lever). The lower end of the lever pushes against the pre-expanded member via at least one intermediate part such as an open or closed push ring.

The lever may therefore have a rounded shape according to the cinematics of the tilting handle and the axial movement of the push ring.

The function of the push ring is to transmit the push forces of the lever and distribute them around the circumference to some extent and to transmit them to the elastic sleeve. The ring is also to protect the product (i.e. elastomeric sleeve) from being touched directly by the lever as well as to avoid relative movement between the product and the lower end of the lever which may cause abrasion or tear. The push ring may be designed to allow for easy removal from the cable after mounting of the elastomeric part (split part design). The holdout tube may have more than one set of engagement features for the lever. This allows to push the product in multiple cycles while engaging with different engagement features. The engagement features are spaced according to the design features of the lever and its cinematics.

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PATENT- UND RECHTSANWALTE The push ring may have force distribution means, such as a flange, on one or both end faces.

The push ring and/or the flange may further have an outline which matches a contour of the elastic sleeve. Furthermore, the push ring may be formed to comprise at least two segments. Thus, the push ring can be deformed to follow a deformation the holdout tube. The shape of the pins and of the holes may have some design features to improve over just straight bolts and cylindrical holes to reduce the risk of disengagement of the lever and holdout tube while operating it.

A further design comprises hook-like protrusions which are built into the holdout tube. The lever has a transversally oriented element such as a metal pin to engage with the hooks. This design, in general, allows for a much larger tilting angle than providing holes and pins.

Thus, improved handling can be achieved through generating sufficient forces to initiate the axial push-off movement of the expanded member on the holdout and allowing multiple engagement positions to increase the push-off length.

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PATENT- UND RECHTSANWALTE REFERENCE NUMERALS

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PATENT- UND RECHTSANWALTE