ACTUATING DEVICE

Abstract: An actuating system for a bobbin tube gripper comprising resilient means held in compression to create a force for urging tube gripping elements into engagement with a tube to be gripped, characterized in that the resilient means comprises a body of porous elastomer.

Description: The present invention relates to actuating systems for bobbin tube gripping devices, particularly but not exclusively for securing bobbin tubes relative to chuck structures in filament winding machines. The actuating system and bobbin tube gripping device described herein are designed particularly, but not exclusively, for use in chucks according to a copending patent applica­ tion filed in Great Britain in the names of the present applicants on 2nd October 1985 under the number and entitled "Chuck Structures". The full disclosure of that copending application is incorporated in the present specification by reference. Prior Art It is conventional practice to provide a chuck in a filament winder with a bobbin tube gripping device com­ prising a wedging "cone" (frusto-conical body) which is axially movable in order to urge gripping elements ra­ dially outwardly into engagement with the internal sur­ face of a bobbin tube to be gripped. Such devices are shown, by way of example only, in United States patent specifications numbers 3052420; 3554455 and 4068806. The cone must be moved in the opposite direction in order to permit the gripping element to return radially inwardly in order to release a previously gripped tube. Alternative systems are shown in US 3815836 and US 4336912; the "wedging" devices are not cone-shaped in these cases. It is also normal practice to urge the wedging devices in the operating (gripping) direction by means of a me­ chanically generated biasing force. Thus, in the ab­ sence of a specially applied releasing force, the tube gripping elements are normally pressed outward in a gripping direction. Suitable means are of course provi­ ded to limit their movement in that direction in the ab­ sence of a bobbin tube to be gripped. The release force is normally applied by a pressure-fluid operated device, such as a piston and cylinder unit. The mechanical biasing force is conventionally produced by a spring device, and such devices have frequently been in the form of so-called "cup- springs" or "Belle­ ville washers". Such spring devices normally comprise a plurality of spring elements, each in the form of a con­ cave/convex disk arranged side by side axially, with each disk contacting one neighbour at its outer rim (on the concave side) and the other neighbour at its inner rim (on the convex side). Spring devices of this type lead to a number of problems as winding speeds increase. Firstly, there is the problem of unbalance in the chuck structure. A degree of play is necessary at the assembly stage in order to enable insertion of the spring devices into the remainder of the structure. This leads to prob­ lems in centering the de-vices relative to the chuck structure, and can lead to shifts of individual elements from the desired positions relative to their neighbours. The resulting slight imbalance is normally acceptable at lower winding speeds (linear thread speed up to about 4'000 meters per minute), but leads to increasing prob­ lems at higher winding speeds. Secondly there is the problem of the large number of elements required to provide the relatively high grip­ ping forces which must be produced at higher winding speeds. This problem has a number of aspects. An in­ creasing number of elements takes up additional space within the chuck structure. Furthermore, an increasing number of elements makes it difficult to maintain uni­ formity of spring characteristics of the individual ele­ ments. As a result, some elements may "collapse" when the device is loaded, and this produces a non-uniform spring characteristic for the device as a whole. Fur­ ther, as the number of elements in the device rises above 20 to 30, careful checking becomes necessary in order to ensure that the correct number of elements is inserted into each device. Finally, the cost of the de­ vice as a whole becomes significant as the number of elements is substantially increased. The invention The present invention provides an actuating system for a bobbin tube gripper comprising resilient means held in compression to create a force for urging tube gripping elements into engagement with a tube to be gripped. The system is characterized in that the resil­ ient means comprises a body of porous elastomer. In the preferred embodiment, the body is made up of a plurality of elements formed individually and arranged side by side in the compression direction. Each element is preferably in the form of a disk or a ring. Such elements can be made with substantially standard dimensions which can be chosen to enable main­ tenance of substantially uniform material quality throughout each element. The elastomer should exhibit a high degree of volume compressibility and a high degree of resistance to com­ pression set. Such characteristics are provided by poly­ urethane elastomers. The body may be free to deform elastically in response to forces applied to it is use but, preferably, the body is confined by engagement with relatively rigid members at least in directions in which deformation is likely to occur in use. In a chuck structure, the relevant direc­ tions are radially outwards in relation to the chuck axis, and axially of the chuck. The actuating system according to the invention may be combined with a relatively rigid element movable to com­ press and relax the body of elastomer and operable thereby to force tube gripping elements into contact with a tube to be gripped, or to permit the elements to release such a tube. The relatively rigid element may be a wedging cone (frusto-conical body) operable to force tube gripping elements radially outwardly when itself urged axially under a biasing force created by the body of elastomer. By way of example, embodiments of the invention will now be described with reference to the accompanying diagram­ matic drawings in which Figure 1 is a longitudinal section through a portion of a chuck generally as illustrated in Figure 4 of the co­ pending application referred to above, but modified to include an actuating system in accordance with the pre­ sent invention, Figures 2 and 3 show an axial view and a side view re­ spectively of a resilient element for the system of Fig­ ure 1, and Figure 4 shows the spring characteristic of the system of Figure 1. Apart from the bobbin tube gripper actuating system, the chuck structure illustrated in figure 1 is also illus­ trated in figure 4 of the copending application referred to above. Accordingly, that structure will be dealt with only briefly in the present description. In order to en­ able ready comparison of the disclosures in the two ap­ plications, the reference numerals used in the present application will correspond to those used for similar parts in the copending application, unless a significant difference has been made to enable modification in ac­ cordance with this invention. The chuck shown in figure 1 is assumed to be cantilever­ mounted in a suitable bearing structure (not shown, to the left as viewed in figure 1) to enable rotation of the illustrated structure about a longitudinal chuck axis 20. The main structural member of the cantilever-portion of the chuck (that is the portion of the chuck outside the bearing system) is provided by a tubular portion 22. The diameter of the external surface of tubular portion 22 is selected to enable the chuck to receive bobbin tubes such as those indicated at 26 and 260 in figure 1, as specified by the machine user. The bobbin tubes are mounted on the chuck by sliding them axially along the tubular portion 22 from the free end thereof (not shown, to the right as viewed in figure 1). During a thread winding operation, each bobbin tube 26, 260 must be secured to the chuck structure for rotation therewith about axis 20 to enable a thread package to be formed on each tube. Accordingly, for each bobbin tube there is a pair of bobbin tube gripping devices incorpo­ rated in the chuck structure, only the gripping devices for bobbin tube 26 been illustrated in figure 1. The ma­ jor operating elements of the bobbin tube gripping devi­ ces are mounted in a chamber 30 provided by the interior of hollow tubular portion 22. In figure 1, most of the elements of the devices have been illustrated only in the upper half of the figure, above the axis 20. It should be understood, however, that the illustrated structure is in fact symmetrical about axis 20, as will appear from the following description. The bobbin tube gripping devices for tube 26 are separa­ ted from each other by an annular bulkhead 86 secured to tubular portion 22 by fixing screws 92. This separation of the two gripping devices ensures that they are inde­ pendently operable, which has certain advantages re­ ferred to in the copending application. Consider first the tube gripping device to the left of bulkhead 86, operating on the inboard portion of bobbin tube 26. The device comprises a set of tube gripping elements 34 extending through respective openings 72 in the tubular portion 22. There may be 8 such elements 34, equiangu­ larly spaced around the axis 20. Each element 34 has a radially outer head portion (not specifically indicated) adapted to engage the internal surface of bobbin tube 26, and a radially inner foot portion (not specifically indicated) adapted to slide on a wedging "cone" (frusto­ conical body) 76. Movement of cone 76 axially of the chuck in one direction (to the left as viewed in figure 1) will force the associated elements 34 radially out­ wardly into contact with the bobbin tube 26, and move­ ment of cone 76 axially in the opposite direction will permit elements 34 to move radially inwardly to an ex­ tent sufficient to release tube 26 for removal from the chuck and for replacement by a new bobbin tube to be gripped. Cone 76 forms part of an operating member generally in­ dicated by the numeral 68. Apart from the cone 76, ope­ rating member 68 comprises an annular piston element 74 having an integral axial extension 84, and an annular wall element 96 which is integral with cone 76. Cone 76 is hollow, and its smaller diameter end fits onto exten­ sion 84; the purpose of this arrangement, which is con­ cerned with the assembly of operating member 68 with its set of tube gripping elements 34 within a tubular por­ tion 22, will be described later in this specification. A tube 66, coaxial with tubular portion 22 extends lon­ gitudinally of the chamber 30. Piston element 74 is sealed at its outer edge on the internal surface of tu­ bular portion 22 and at its inner edge on tube 66. It defines one end of a pressurizable compartment 78. Pres­ sure fluid can be fed into this compartment via a pas­ sage provided by the interior of tube 66 and openings 82 in that tube aligned with compartment 78. When that com­ partment is suitably pressurized, piston element 74, and thus cone 76, can be forced to the right as viewed in figure 1, thereby enabling element 34 to move radially inwardly in a direction releasing bobbin tube 26. Normally, however, tube 66 and compartment 76 are not pressurized, and operating member 68 is urged to the left as viewed in figure 1 by a mechanical biasing means provided in a compartment 88 defined between the separa­ ting wall 86 and the wall element 96. The present inven­ tion relates in particular to the formation of this biasing means, which must be arranged to exert a biasing force on wall element 96 urging it to the left as viewed in figure 1, thereby causing cone 76 to urge tube grip­ ping element 34 in a radially outward direction. In the absence of a bobbin tube 26, this radial outward move­ ment of elements 34 is limited by suitable projections (not shown) on those elements preventing their ejection from the chuck structure. Before turning to a detailed discussion of the biasing means, the second bobbin gripping device for tube 26 will be described briefly. As will be readily apprecia­ ted from figure 1, this second bobbin gripping device is essentially a mirror image of the first, considered with reference to a plane at right angles to the axis 20 and through the mid-point of bulkhead 86. Thus, the second bobbin gripping device comprises a second set of tube gripping elements 34 cooperating with the outboard por­ tion of bobbin tube 26; an operating member 70 compri­ sing a cone 100 (similar to but facing in the opposite direction from cone 76), an annular piston element 98 and an annular wall element 102; a pressurizable com­ partment 104, one side of which is defined by piston element 98 and which can be pressurized at the same time as compartment 78 via tube 66 and openings 108 therein; finally, a compartment 90 defined between bulkhead 86 and wall element 102 which contains a second biasing means the same in all essential respects as that con­ tained within the compartment 88 and described imme­ diately below. It will be noted that wall elements 96, 102 are a sliding fit at their outer edges on the inter­ nal surface of tubular portion 22, and at their inner edges on a tube 94 which is integral with bulkhead 86 and is a sliding fit on the central tube 66. The axial end faces of tube 94 provide respective endstops for the tube-release movements of piston elements 74, 98 respec­ tively. The biasing means in compartment 88 (that in compartment 90 is the same) comprises an annular body of resiliently compressible material substantially filling the whole volume of the compartment. In the embodiment illustrated in figure 1, this body of resilient material is made up of 6 rings 870 mounted axially side by side on tube 94 and engaging the internal surface of tubular portion 22 at their outer edges. An individual ring 870 is shown in figures 2 and 3 in an uncompressed condition having an internal diameter s, an external diameter d and an axial thickness T. Such rings can be readily manufactured from standard sheets of suitable material so as to provide uniform material quality in each ring 870. 6 rings have been shown by way of example only in figure 1; there may be more or less as required by the circumstances. If the material quality can be adequately controlled over an appropriate length, then the rings may be combined to a single sleeve filling compartment 88. Each ring 870 is made of a porous elastomer having a high degree of volume compressibility and a lower degree of compression set. Polyurethane elastomers are particu­ larly advantageous in this respect. For all possible po­ sitions of wall element 96 relative to bulkhead 86 in the assembled chuck, each ring 870 is in a state of axial compression when compared with its "normal" or "relaxed" condition illustrated in figures 2 and 3. This is indicated in figure 1 by the axial thickness t of each ring 870 (t being less than T). The external dia­ meter L of the tube 94 may be equal to, greater than or less than S and the internal diameter D of the tubular portion 22 may be equal to, less than or greater than d. Rings 870 can be mounted on tube 94 and within tubular portion 22 in the relaxed condition, and can be com­ pressed in situ after assembly with the other parts of the chuck structure. Complete filling of compartment 88 by the resilient material is not an essential feature of the invention, but it is highly desirable. Extension of the body of resilient material between the rigid end members (bulkhead 86 and wall element 96) is of course essential. A less than complete filling of compartment 88 therefore represents a radial gap at the inner edge of each ring, or at the outer edge or both. This leads to incomplete exploitation of the space available in compartment 88 and a higher loading per unit area of cross section of the body of resilient material. Fur­ thermore, if the body of resilient material is deform­ able under centrifugal forces which may arise in use, and a gap is present at standstill between the outer edges of the rings and the wall surrounding compartment 88, then the rings may deform unevenly in operation and cause inbalance in the chuck structure as a whole. Ac­ cordingly, at least contact at the outer edges of the rings with the tubular portion 22 is an extremely desir­ able feature. The material to be used in the rings is chosen by refe­ rence to the required performance characteristic of the biasing means. Such a performance characteristic is shown in graphical form in figure 4 in which the hori­ zontal axis represents axial compression c (in terms of distance or proportion of relaxed length or any other convenient unit) of the body of resilient material as a whole and the vertical axis represents the resultant force F applied by the compressed body of resilient ma­ terial to the wall element 96. This latter force repre­ sents the axial force available to wedge gripping ele­ ments 34 outwardly into contact with bobbin tube 26. For a given chuck design, a design characteristic DC can be defined for the body of resilient material. This de­ sign characteristic is derived from the physical charac­ teristics and required performance of the chuck itself, and must be established on a case to case basis. In ge­ neral, the required force F will be dependent upon the size of thread packaege which must be wound upon the chuck and the available compression will be given by the dimensions of the cone 76 and a required radial movement of the elements 34, bearing in mind the practical varia­ tion in nominal internal diameters of bobbin tubes 26 with which the chuck has to operate in use. Figure 4 assumes a linear characteristic DC. This is not essen­ tial, but will be assumed for convenience of descrip­ tion. As indicated on figure 4, there are three significant points on the design characteristic DC. At the first point (compression c 1, axial force F 1) the degree of compression c 1 is at its operational minimum (volume of compartment 88 at its operational maximum) corresponding to a bobbin tube 26 with the maximum designed internal diameter. The "spring characteristic" of the body of re­ silient material must be such that under these condi­ tions a minimum axial force F 1 is exerted (to the left) on the wall element 96, so that tube element 34 can exert a predetermined (corresponding) minimum gripping force on the bobbin tube 26. In the absence of a tube 26, the resilient material can expand compartment 88 still further (further reduce compression c) until the retaining stops on element 34 engage the tubular portion 22. The applied axial force F on wall element 96 will then drop below the level F 1, but this is not opera­ tionally significant, because no gripping operation is performed under these conditions. The second significant point (compression c 2, axial force F 2) respresents a movement of wall element 96 to the right as viewed in figure 1 with radial retraction of elements 34 to engage the internal surface of a bob­ bin tube 26 of the minimum designed internal diameter. The corresponding axial force F 2 must be such that the elements 34 do not penetrate unduly into the wall thick­ ness of bobbin tube 26, thereby damaging the tube. This consideration may become even more relevant in the course of a package winding operation than at the time of first contact of element 34 with tube 26, as will be­ come clear from the immediately following discussion of the third significant point (compression c3, axial force F 3). Compression c 3 represents a movement of wall element 96 to the right, and a corresponding radially inward move­ ment of element 34, to ensure that the gripping elements will effectively release a bobbin tube carrying a wound package for removal of the package and replacement thereof by a fresh bobbin tube. The degree of compres­ sion required form this purpose depends to a large extent upon the winding operation itself. Thus, if a thread is wound under substantial tension to form a large thread package, then the bobbin tube 26 is compressed radially inwardly during the package winding operation. As indi­ cated in figure 1, the bobbin tube surface is normally spaced from the outer surface of tubular portion 22 at the start of a winding operation because of the slight projection of element 34 beyond the cylindrical outer surface of portion 22. The compression of the bobbin tube during a winding operation can, however, force the internal surface of the tube into contact with the ex­ ternal surface of chuck portion 22. As previously indi­ cated, axial forces within the range F 2 to F 3 must be such that there is no undue penetration of gripping ele­ ment 34 into the wall thickness of bobbin tube 26 - the elements 34 should "give" as the bobbin tube is compressed. As will be described later in this specification, for the embodiment illustrated in figure 1, a fourth signi­ ficant point (not shown) can be identified on the design characteristic DC. Since this point is related to the assembly of the illustrated embodiment, and not to the operation in use, description of this aspect will be de­ layed until the assembly process itself is described. When a design characteristic DC has been established, it must be compared with the spring characteristics from materials suppliers to enable selection of an appropri­ ate "shortlist" of materials. The final choice of mate­ rial will, however, take other factors into account de­ pending upon the required circumstances of use, for ex­ ample compression set (this is an ageing effect under which the material loses some of its resilience when compressed continuously over a period of time - it is of significance in relation to the required lifespan of the biasing means), resistance to substances which may pene­ trate compartment 88 in use or which may be present du­ ring the assembly stage, for example oils, acids, etc., response of the material (in terms of radial expansion) to centrifugal forces in use, etc. If the compartment is not completely filled by the resilient material, then the ability of the body of material to resist transverse bending under axial load may also be significant, depen­ ding upon the play available bet-ween the body of mate­ rial and its transverse guiding / confining surfaces. For this reason also, it is preferred that the body of material is effectively guided (e.g. by contact with tube 94 at its inner edge) and / or confined (e.g. by contact with the internal surface of tubular portion 22). A polyurethane elastomer supplied by Getzner Chemie GmbH of Bludenz-Buers in Austria under the regi- stered trademark SYLONER has proved to be suitable. From the range of materials supplied by Getzner Chemie under the trademark, the "S" type is preferred. The material is available in a sheet form suitable for formation of rings 870. According to the data available from the suppliers, this material is suitable for elastic deformation of up to 40 % of the original sheet thickness. Purely by way of example, the following data relate to a practical design using the "SYLONER" material in a chuck designed for use with bob­ bin tubes having nominal internal diameter of 75 mm. Internal diameter of tubular portion 22: 57 mm. Maximum length of compartment 88 (90) 60 mm. Travel of wall portion 96 (102) corresponding to the shift from point c 1 to point c 2 in figure 4: 3.3 mm. Travel of wall portion 96 (102) corresponding to the shift from point c 2 to point c 3 in figure 4: 4.7 mm. Number of elastomeric rings (870, figure 1): 8 (4). Axial thickness T (figure 3) of each ring in the relaxed (uncompressed) condition: 11 mm (22 mm). External diameter d (figure 2) of each ring in the re­ laxed condition: 52 mm. Internal diameter s (figure 2) of each ring in the re­ laxed condition: 15 mm Material type: SYLOMER SB As indicated in this list, the total, uncompressed axial length of the body of material provided by these rings 870 is 88 mm and this can be made up alternatively by 8 rings of 11 mm each or 4 rings of 22 mm each. The degree of radial expansion of each ring under the compression produced in compartment 88 (90) even in the maximum-vol­ ume condition of the compartment is sufficient to cause firm contact between the outer cylindrical surface of each ring and the internal surface of tubular portion 22. This chuck design is intended for rotation about axis 20 to enabling take-up of thread at linear speeds up to 6000 n/min. Centrifugal forces acting on the rings 870 tend to deform the material radially outwardly against the tubular portion 22. Since the rings are already in contact with tubular portion 22 even at standstill, such additional radial deformation is not possible, and the resultant effect is an increase in the axial force ap­ plied to wall portion 96. This is an additional reason for preference for guiding contact of the rings with the tubular portion 22 rather than with tube 94. Due to the centrifugal forces arising in operation, and the resul­ tant deformation of the resilient material, contact with the internal tube 94 can be lost. The chuck design described above is suitable for a chuck length in cantilever, tubular portion 22 of approxi­ mately 600 mm. An alternative design, suitable for a corresponding length of approximately 900 mm and usable with bobbin tubes of nominal internal diameter 94 mm is given below: Internal diameter of tubular portion 22: 75 mm Maximum length of compartment 88 (90): 48.2 mm Number of rings (870, figure 1) of elastomeric material: 3 Axial thickness T (figure 3) of each ring in its relaxed condition: 21 mm External diameter d (figure 2) of each ring in its re­ laxed condition: 67 mm Internal diameter s (figure 2) of each ring in its re­ laxed condition: 15 mm Material type: SYLOMER S Travel of wall portion 96 (102) corresponding to shift from point c 1 to point c 2 in figure 4: 3.3 mm Travel of wall portion 96 (102) corresponding to shift from point c 2 to point c 3 (figure 4): 9.4 mm This chuck is also designed for take-up of thread at linear speeds up to 6000 n/min. As in the case of the previous design, the compression of the resilient mate­ rial even in the maximum-volume condition of compartment 88 (90) is such that the external cylindrical surface of each ring contact the internal surface of tubular por­ tion 22. Further, as noted above, the contact pressure between the resilient material and the internal surface of tubular portion 22 is increased at operating speed due to centrifugal force. On the other hand, the resilient material is required to "work" slightly in the compartment 88 (90) even during a given winding operation, e.g. because of return of the tube gripping elements 34 radially into the tubular portion 22 as a gripped tube 6 is overwound during package for­ mation. It is important that the fiction arising between each ring 870 and tubular portion 22 should not inter­ fere with this "working". In order to avoid such inter­ ference, it may be desirable to provide a lubricant (e.g. a silicon oil or grease) between the internal sur­ face of tubular portion 22 and the external surface of the body of resilient material made up by rings 870. The "release" force required to overcome the biasing force applied from compartment 88 (90) is provided by pressurization of compartment 78 (104) from tube 66. The maximum degree of compression of the resilient material by pressurization of compartment 78 (104) is limited by engagement of piston element 74 (98) with an axial end­ stop provided in the embodiment of figure 1 by the adja­ cent axial endface on tube 94. As will now be described, for purposes of assembly, the resilient material is re­ quired to withstand a degree of compression greater than that represented by point c 3, F 3 in figure 4. The internal components of the chuck (that is, the com­ ponents retained within tubular portion 22) are mounted in the tubular portion by insertion through the open, free and (not shown - to the right in figure 1). In the course of assembly of the components already described with reference to figure 1, gripping elements 34 of the device 68 can be located in their respective openings 72 before insertion of the cone 76 and assembly thereof with the axial projection 84 on the preassembled piston 74. However, cone 100 in the device 70 must be inserted into the tubular portion 22 before the corresponding gripping elements 34. In order to provide sufficent space for location of elements 34 of device 70 in the respective openings 72, wall element 102 must be pressed in the axial direction towards bulkhead 86 to produce a relatively high degree of compression of the rings 870 in compartment 90. The characteristic DC (figure 4) of the resilient material must therefore permit a fourth significant point c 4 F 4 to the right of those illustrated in figure 4 corresponding to this degree of "assembly compression". The combination of the pressurizable compartment 78 (104), moving member 68 (70), confining compartment 88 (90) and the resilient material made up by the rings 870 constitutes an actuating system. This system in turn is part of a bobbin tube gripper comprising two such sys­ tems (to either side of bulkhead 86 in figure 1) and the tube gripping elements 34 associated therewith. Only the one tube gripper, associated with the inboard bobbin tube 26, has been shown in figure 1; for each other bob­ bin tube, e.g. tube 260 shown in figure 1, a similar, individual tube gripper must be provided. In the embodi­ ment illustrated in figure 1, the gripper for tube 26 is separated from that for tube 260 by a unit 106 which is not relevant to the present invention and will not be described herein. The unit is, however, described in full in the copending patent application referred to above. To the right of unit 106 the inboard end of the pressurizable compartment 78 A of the tube gripper associated with bobbin tube 260 can be seen. The tube 66 supplying pressure air to the pressurizable compartment is common to all of the bobbin tube grippers. The invention is not limited to details of the illustra­ ted embodiment. The chuck design in particular has been shown only by way of example - the invention is applica­ ble to radially different designs. The choice of mate­ rial for the resiliently compressible means is not limi­ ted to polyurethane elastomers - other porous elastomers providing equivalent or better properties relevant to this mode of use can be substituted. The ring elements in Figs 2 and 3 do not have cylindri­ cal inner and outer surfaces. For example, the outer surface could be provided with a plurality of recesses, preferably evenly distributed around the axis of the ring. Due to compression during assembly, the recesses may be "filled" when each ring is in place in the chuck structure but this may not be essential provided adequate centering effect is available from the contact (with tubular portion 22) actually produced.

Claims: 1. An actuating system for a bobbin tube gripper compri­ sing resilient means held in compression to create a force for urging tube gripping elements into engage­ ment with a tube to be gripped, characterized in that the resilient means comprises a body of porous elas­ tomer. 2. A system as claimed in claim 1 wherein the body is made up of a plurality of elements formed individual­ ly and arranged side by side in the compression di­ rection. 3. A system as claimed in claim 2 wherein each element is in the form of a disk or a ring. 4. A system as claimed in any preceding claim wherein the elastomer exhibits a high degree of volume com­ pressibility and a high degree of resistance to com­ pression set. 5. A system as claimed in claim 4 wherein the elastomer is a polyurethane elastomer. 6. A system as claimed in any preceding claim wherein the body is confined by engagement with relatively rigid members at least in directions in which defor­ mation is likely to occur in use. 7. An actuating system according to any preceding claim in combination with a relatively rigid element mova­ ble to compress and relax the body of elastomer and operable thereby to force tube gripping elements into contact with a tube to be gripped, or to permit the elements to release such a tube. 8. A combination as claimed in claim 7 wherein the rigid element is a wedging cone operable to force tube gripping elements radially outwardly when itself urged axially under a biasing force created by the body of elastomer. 9. In or for a winding machine, a chuck including a com­ bination as defined in claim 7 or claim 8.

Inventors: HOLBEIN, ERWIN, MUTTER, HEINZ, SCHNEEBERGER, RUEDI
Applicants: MASCHINENFABRIK RIETER AG
Application year: 1986
Main classification: B65H75
IPC codes: B65H54