CROSS REFERENCE TO RELATED APPLICATION 
   The present application claims priority from German Patent Application No. 10 2004 035 771.4 dated Jul. 23, 2004, the entire disclosure of which is incorporated herein by reference. 
   BACKGROUND OF THE INVENTION 
   The invention relates to an apparatus at a carding machine, for example but not exclusively, a carding machine having a cylinder which has a cylindrical, clothed wall surface and at least two radial cylinder ends, and having at least one clothed and/or unclothed machine element located opposite the cylinder clothing at a spacing therefrom and two stationary side screens, on which there are mounted holding devices for work elements, for example sliding bends, stationary carding elements, cylinder coverings, which in use are subjected to heat. 
   The effective spacing of the tips of a clothing from a machine element located opposite the clothing is called a carding nip. The said machine element can also have a clothing but could, instead, be formed by an encasing segment having a guide surface. The carding nip is decisive for the carding quality. The size (width) of the carding nip is a fundamental machine parameter, which influences both the technology (the fibre processing) and also the running characteristics of the machine. The carding nip is set as narrow as is possible (it is measured in tenths of a millimeter) without running the risk of a “collision” between the work elements. In order to ensure that the fibres are processed evenly, the nip must be as uniform as possible over the entire working width of the machine. 
   The carding nip is especially influenced, on the one hand, by the machine settings and, on the other hand, by the condition of the clothing. The most important carding nip in a carding machine having a revolving card top is located in the main carding zone, that is to say between the cylinder and the revolving card top unit. At least one of the clothings bounding the work spacing is in motion, usually both. In order to increase the production of the carding machine, endeavours are made to make the speed of rotation or velocity of the moving elements, in use, as high as fibre processing technology will allow. The work spacing changes as a function of the operational conditions, the change occurring in the radial direction (starting from the axis of rotation) of the cylinder. 
   In carding, larger amounts of fibre material are increasingly being processed per unit time, which results in higher speeds for the work elements and higher installed capacities. Increasing fibre material throughflow (production) leads to increased generation of heat as a result of the mechanical work, even when the work surface remains constant. At the same time, however, the technological result of carding (web uniformity, degree of cleaning, reduction of neps etc.) is being continually improved, leading to more work surfaces in carding engagement and to closer settings of those work surfaces with respect to the cylinder (drum). The proportion of synthetic fibres being processed is continually increasing, with more heat, compared with cotton, being produced as a result of friction from contact with the work surfaces of the machine. The work elements of high-performance carding machines today are fully enclosed on all sides in order to meet the high safety standards, to prevent emission of particles into the spinning room environment and to minimise the maintenance requirement of the machines. Gratings or even open material-guiding surfaces, which allow an exchange of air, belong to the past. As a result of the circumstances mentioned, there is a marked increase in the input of heat into the machine whereas there is a marked decrease in the heat removed by means of convection. The resulting increase in the heating of high-performance carding machines results in greater thermoelastic deformations, which, because of the unequal temperature field distribution, influence the set spacings of the work surfaces: the spacings between the cylinder and the card top, doffer, fixed card tops and separating-off locations decrease. In extreme cases, the nip set between the work surfaces can be completely used up as a result of thermal expansion so that components in relative motion collide, causing major damage to the high-performance carding machine concerned. Additionally, it is especially possible for the generation of heat in the work region of the carding machine to result in different thermal expansions when the temperature differences between the components are too large. 
   In a known apparatus (EP 0 446 796 A), all parts influencing the work spacing (for example, the cylinder and the card top bars) are preferably fabricated from a material having a high elasticity modulus in order to reduce sagging over the working width. Such a material is, for example, steel or fibre-reinforced plastics material. The material selected has to ensure the desired dimensional accuracy of the part (in the case of the manufacturing procedure in question) and has to be able to maintain that in use. The material should accordingly exhibit less thermal expansion and/or greater thermal conductivity so that heat losses which occur (which are unavoidable at high production rates) do not result in disruptive deformation of the work elements. In the case of the known apparatus, the thermal expansion of the co-operating components influencing the work spacing, namely that of the cylinder (drum) and of the card top bars, is equal and homogeneous, because the components are made of the same material. Even though the material should exhibit less thermal expansion, the carding nip is reduced in undesirable manner—albeit to a small extent—which results in problems ranging from reduced carding quality to disruptions in operation. In addition, it is disadvantageous that widening of the cylinder as a result of centrifugal force cannot be reduced or avoided by the known measures. 
   It is an aim of the invention to provide an apparatus of the kind mentioned at the beginning that avoids or mitigates the mentioned disadvantages and that especially makes possible a carding nip or work spacing, between the cylinder clothing and the clothed and/or not clothed counterpart element, that remains constant or virtually constant when heat is generated. 
   SUMMARY OF THE INVENTION 
   The invention provides a carding machine having a carding nip and a plurality of machine elements that influence the carding nip, in which at least first and second machine elements influencing the carding nip are constructed to have thermal expansion characteristics which are such that when the first and second machine elements are subjected to heat generated in operation of the carding machine, the carding nip remains substantially constant. 
   In one preferred embodiment, the machine comprises first and second elements influencing the carding nip which are so constructed that, when subjected to heat generated in operation, they undergo no thermal expansion. In another preferred embodiment, at least one of said machine elements undergoes negative thermal expansion when subjected to heat in use. In a further preferred embodiment, at least one of said machine elements undergoes positive thermal expansion when subjected to heat in use. 
   In accordance with a first aspect of the invention, the parts influencing the carding nip (work spacing) (for example, the cylinder, the carding bars and the holding elements for the carding bars) are so constructed that they exhibit no, or virtually no, thermal expansion under the heat of operation. As a result, the carding nip does not change. In accordance with a second aspect of the invention, at least one part influencing the carding nip exhibits negative thermal expansion (contraction) so that a change in the carding nip caused, for example, by positive thermal expansion of a part influencing the carding nip is compensated. This is especially the case when the carding-nip-influencing carrying elements provided with clothings are located opposite one another and one carrying element, for example the cylinder, undergoes positive expansion as a result of heating and the other carrying element, for example the carding bars (card top bars), in contrast undergoes negative expansion, that is to say contracts and, to a certain extent, recedes. In accordance with a third aspect of the invention, at least one part influencing the carding nip exhibits positive thermal expansion (widening) so that a change in the carding nip caused, for example, by positive thermal expansion of a part influencing the carding nip is likewise compensated. This is especially the case when the carding-nip-influencing carrying elements are arranged next to one another and one carrying element, for example the cylinder, undergoes positive expansion as a result of heating and the other carrying element, for example the flexible bends, likewise undergoes positive expansion, that is to say becomes wider and as a result raises the card top bars relative to the cylinder. According to all three aspects of the invention, the carding nip remains the same or virtually the same in use. 
   Advantageously, a part influencing the carding nip, for example a flexible bend, is so constructed that it exhibits positive thermal expansion in use. Preferably, a part influencing the carding nip, for example a card top bar, is so constructed that it exhibits negative thermal expansion in use. Advantageously, the positive thermal expansion of a part influencing the carding nip is compensated by the negative thermal expansion of the corresponding counterpart element. Preferably, a part influencing the carding nip is so constructed that it exhibits no thermal expansion in use. Preferably, the carding nip is influenced by the cylinder and the at least one carding element. Advantageously, the carding nip is influenced by the holding device for the at least one carding element. Preferably, the holding device for the at least one carding element is formed by at least one element of the side part. Advantageously, the side part consists of a side screen and at least one guide element (flexible bend). Preferably, the side part consists of a side screen and at least one extension bend. Advantageously, the clothed machine elements are revolving card tops. Preferably, the clothed machine elements are stationary card tops. Advantageously, the cylinder is made, at least in part, of steel. Steel ensures the stability of the cylinder and has relatively high resistance to bending. Preferably, the cylinder is made, at least in part, of aluminium. Aluminium likewise ensures the stability of the cylinder and has a relatively low specific weight. Preferably, the material for the parts influencing the carding nip is, at least in part, a carbon fibre-reinforced plastics material (CFRP). Carbon has a density of 1.45 g/cm 3 . The basic material comprises carbon fibres. The latter can be produced from plastics filaments, which are heated in the absence of air and consequently “carbonised”. For example, they have a diameter of 0.007 mm. These fibres are embedded in a carrier substance (matrix) of synthetic resins. The forces acting on carbon fibres are taken up by the fibres substantially only in the line of force flux. The fibres are therefore mainly laid in parallel. If bending and torsional stresses do not come from just one direction, individual layers of fibres are advantageously placed on top of one another in different orientations. Preferably, the thermal expansion coefficient of the carbon fibre reinforced plastics material (CFRP) is adjustable. Zero adjustment means no change and negative adjustment results in contraction so that no thermal expansion or negative thermal expansion of the component(s) is produced. By that means, the materials of the cylinder and, for example, the side parts are so matched to one another that, under the heat acting on the parts influencing the carding nip in use, the carding nip remains constant. Advantageously, the cylinder of the carding machine comprises a metal cylinder and at least one circular cylindrical sheath made of carbon fibre reinforced plastics material (CFRP) surrounding the cylinder. Preferably, the flexible bend and/or the extension bend is/are made at least in part of carbon fibre reinforced plastics material (CFRP). Advantageously, the flexible bend and/or the extension bend is provided with a support (layer) of carbon fibre reinforced plastics material (CFRP). Preferably, the cylinder is made of a metallic material, for example steel, and the flexible bend and/or the extension bend is/are made at least in part of carbon fibre reinforced plastics material (CFRP). Advantageously, the card tops, for example revolving and/or stationary card tops, are made at least in part of carbon fibre reinforced plastics material (CFRP). Preferably, the side screen is made at least in part of carbon fibre reinforced plastics material (CFRP). Advantageously, at least one metal cylinder and at least one circular cylindrical sheath made of carbon fibre reinforced plastics material (CFRP) surrounding the cylinder are provided. Preferably, the metal cylinder and the sheath are mutually biased at room temperature and at operating temperature. Advantageously, the metal cylinder is subjected to compressive stresses and the sheath is subjected to tensile stresses in the circumferential direction. Preferably, the reinforcement fibres of CFRP in the sheath are oriented in the circumferential direction of the cylinder. As a result, widening of the cylinder as a result of centrifugal force is especially advantageously reduced or avoided, especially at high speeds of rotation. Advantageously, the cylinder is enclosed. Preferably, the removal of heat from the cylinder is different to that from the side parts. Advantageously, the roller is a licker-in of a flat card or roller card. Preferably, the roller is the doffer of a flat card or roller card. 


   
     BRIEF DESCRIPTION OF THE DRAWINGS 
       FIG. 1  is a diagrammatic side view of a carding machine with an apparatus according to the invention; 
       FIG. 2  shows card top bars of the revolving card top of the carding machine of  FIG. 1  and portions of a slideway, of the flexible bend, of the side screen and of the cylinder, and also the carding nip between the clothings of the card top bars and the cylinder clothing; 
       FIGS. 3   a ,  3   b  show sections through a roller comprising a metal cylinder and a circular cylindrical sheath made of carbon fibre reinforced plastics material surrounding the cylinder, in a front view ( FIG. 3   a ) and side view ( FIG. 3   b ); 
       FIG. 4  is a diagrammatic section through a slideway along the line I-I in  FIG. 2  together with flexible bends and side screens; 
       FIG. 5  is a side view of a part of a side screen and flexible bend, cylinder, extension bend, stationary carding element and revolving card top bars; 
       FIG. 6  is a side view of a flexible bend according to the invention; 
       FIG. 7  is a side view of an extension bend according to the invention in the pre-carding zone; and 
       FIG. 7   a  shows the carding nip between the clothing of a stationary carding element according to the invention and the cylinder clothing. 
   


   DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS 
     FIG. 1  shows a carding machine  47 , for example a TC 03 carding machine made by Trützschler GmbH &amp; Co. KG of Mönchengladbach, Germany, having a feed roller  1 , feed table  2 , lickers-in  3   a ,  3   b ,  3   c , cylinder  4 , doffer  5 , stripper roller  6 , nip rollers  7 ,  8 , web-guiding element  9 , web funnel  10 , draw-off rollers  11 ,  12 , revolving card top  13  having card-top-deflecting rollers  13   a ,  13   b  and card top bars  14 , can  15  and can coiler  16 . Curved arrows denote the directions of rotation of the rollers. Reference letter M denotes the centre (axis) of the cylinder  4 . Reference numeral  4   a  denotes the clothing and reference numeral  4   b  denotes the direction of rotation of the cylinder  4 . Reference letter B denotes the direction of rotation of the revolving card top  13  at the carding location and reference letter C denotes the direction in which the card top bars  14  are moved on the reverse side. Reference numerals  23 ′,  23 ″ denote stationary carding elements and reference numeral  39  denotes a cover underneath the cylinder  4 . Arrow A denotes the work direction. 
   In accordance with  FIG. 2 , on each side of the carding machine, a flexible bend  17  having several adjustment screws is fixed laterally to the side screen  19   a ,  19   b  (see  FIG. 4 ). The flexible bend  17  has a convex outer surface  17   a  and an underside  17   b . On top of the flexible bend  17  there is a slideway  20 , for example made of low-friction plastics material, which has a convex outer surface  20   a  and a concave inner surface  20   b . The concave inner surface  20   b  rests on top of the convex outer surface  17   a  and is able to slide thereon in the direction of arrows D, E. Each card top bar consists of a rear part  14   a  and a carrying member  14   b . Each card top bar  14  has, at each of its two ends, a card top head, each of which comprises two steel pins  14   1 ,  14   2 . Those portions of the steel pins  14   1 ,  14   2  that extend out beyond the end faces of the carrying member  14   b  slide on the convex outer surface  20   a  of the slideway  20  in the direction of the arrow B. A clothing  18  is attached to the underside of the carrying member  14   b . Reference numeral  21  denotes the circle of tips of the card top clothings  18 . The cylinder  4  has on its circumference a cylinder clothing  4   a , for example a sawtooth clothing. Reference numeral  22  denotes the circle of the tips of the cylinder clothing  4   a . The spacing (carding nip) between the circle of tips  21  and the circle of tips  22  is denoted by reference letter a and is, for example, 3/1000″. The spacing between the convex outer surface  20   a  and the circle of tips  22  is denoted by reference letter b. The spacing between the convex outer surface  20   a  and the circle of tips  21  is denoted by reference letter c. The radius of the convex outer surface  20   a  is denoted by reference letter r 1  and the radius of the circle of tips  22  is denoted by reference letter r 2 . The radii r 1  and r 2  intersect at the centre point M of the cylinder  4 . Reference numeral  19  denotes the side screen. 
   The high-speed roller shown in  FIGS. 3   a ,  3   b  for a fibre-processing machine, for example a cylinder  4  of a carding machine, consists of a hollow cylindrical roller body  30  and two roller ends  31   a ,  31   b  at the end faces. The roller ends  31   a ,  31   b  advantageously are made of metal, for example steel or aluminium. Reference numeral  32  denotes a spoke, reference numeral  33  a hub and reference numeral  34  an end flange. The roller body  30  consists of an internal steel cylinder  35  and an external hardened CFRP sheath  36 . The CFRP sheath  36  has the shape of a thin-walled hollow cylinder. At operating temperature, in the biased state, compressive stresses are present in the circumferential direction in the cylindrical wall region of the steel cylinder  35  and tensile stresses in the cylindrical CFRP sheath  36 . In use, because of the centrifugal force to which the steel cylinder  35  is subjected, the compressive stresses are reduced. The thermal expansion coefficient of the cylinder material is much greater than the thermal expansion coefficient of the carbon fibre reinforced plastics material in the direction of the reinforcement fibres; for example, the thermal expansion coefficient α of steel is between 11×10 −6  1/K and 17×10 −6  1/K and that of CFRP in the fibre direction is about zero, especially between −2×10 −6  1/K and +2×10 −6  1/K. When subjected to heat in use, the internal diameter of the CFRP sheath  36  accordingly changes only very slightly, whereas the thermal expansion of the steel cylinder  35  is considerable. The thermal expansion of the CFRP-sheathed steel cylinder  35  is consequently less than the thermal expansion of a cylinder having an all-steel wall. 
   A roller according to the invention, comprising a metal cylinder and a composite fibre sheath, is lighter in comparison to an all-steel or all-aluminium roller, has a reduced mass inertia and exhibits linear thermal expansion which is adjustable (down to negative values) as a result of constructively arranged fibre orientation. The advantages of the roller according to the invention in use, which result from the properties of the material, are, for example, substantially improved braking values, savings in terms of drive units, energy savings, higher production rates, wider working widths and vibration-free running. 
   Density, specific rigidity and specific strength—the table that follows lists the density, modulus of elasticity and strength of the materials in comparison with one another: 
   
     
       
             
             
             
             
             
           
             
             
             
             
             
           
         
             
                 
                 
             
             
                 
                 
               Density 
               Modulus of elasticity 
               Strength 
             
             
                 
               Material 
               (g/cm 3 ) 
               (N/mm 2 ) 
               (MPa) 
             
             
                 
                 
             
           
           
             
                 
             
           
        
         
             
                 
               St 52 
               7.8 
               210 000 
                400 
             
             
                 
               Al 
               2.7 
                70 000 
                350 
             
             
                 
               CFRP 
               1.3 
               75 000 to 180 000 
               1500 
             
             
                 
               GFRP* 
               1.9 
               20 000 to 40 000  
               1250 
             
             
                 
                 
             
             
                 
               *Glass fibre-reinforced plastics material 
             
           
        
       
     
   
   In the direction of the fibres, CFRP has considerable advantages compared to steel (the latter being represented by St 52 in the above table). The individual fibres made up into a tube in the course of a winding process determine the anisotropic (directionally dependent) behaviour of such a tube. 
     FIG. 4  shows part of the cylinder  4  together with the cylindrical surface  4   f  of its wall  4   e  and the cylinder ends  4   c ,  4   d  (radial supporting elements). The surface  4   f  is provided with a clothing  4   a , which in this example is provided in the form of wire with sawteeth. The sawtooth wire is drawn onto the cylinder  4 , that is to say is wound around the cylinder  4  in tightly adjacent turns between side flanges (not shown), in order to form a cylindrical work surface provided with tips. Fibres should be processed as evenly as possible on the work surface (clothing). The carding work is performed between the clothings  18  and  4   a  located opposite one another and is substantially influenced by the position of one clothing with respect to the other and by the clothing spacing a between the tips of the teeth of the two clothings  18  and  4   a . The working width of the cylinder  4  is a determining factor for all other work elements of the carding machine, especially for the revolving card tops  14  or stationary card tops  23 ′,  23 ″ ( FIG. 1 ), which together with the cylinder  4  card the fibres evenly over the entire working width. In order to be able to perform even carding work over the entire working width, the settings of the work elements (including those of additional elements) must be maintained over that working width. The cylinder  4  itself can, however, be deformed as a result of the drawing-on of the clothing wire, as a result of centrifugal force or as a result of heat produced by the carding process. The shaft  25  of the cylinder  4  is mounted in positions (not shown) located on the stationary machine frame  24   a ,  24   b . The diameter, for example 1250 mm, of the cylindrical surface  4   f , that is to say twice the radius r 3 , is an important dimension of the machine and becomes larger in use as a result of the heat of work. The side screens  19   a ,  19   b  are fastened to the two machine frames  24   a  and  24   b , respectively. The flexible bends  17   a  and  17   b  are fastened to the side screens  19   a  and  19   b , respectively. 
   When heat is produced in use in the carding nip a between the clothings  18  (or in the carding nip d between the clothings  23 ′) and the cylinder clothing  4   a  as a result of carding work, especially in the case of a high production rate and/or the processing of synthetic fibres or of cotton/synthetic fibre blends, the cylinder wall  4   e  undergoes expansion, that is to say the radius r 3  increases and the carding nip a (se  FIG. 2 ) or d (see  FIG. 7   a ) decreases. The heat is directed via the cylinder wall  4   e  into the radial carrying elements, the cylinder ends  4   c  and  4   d . The cylinder ends  4   c ,  4   d  likewise undergo expansion as a result thereof, that is to say the radius increases. The cylinder  4  is almost entirely encased (enclosed) on all sides —in a radial direction by the elements  14 ,  23 ,  39  (see  FIG. 1 ) and to the two sides of the carding machine by the elements  17   a ,  17   b ,  19   a ,  19   b ,  24   a ,  24   b . As a result, scarcely any heat is radiated from the cylinder  4  to the outside (to the atmosphere). Nevertheless, the heat of the cylinder ends  4   c ,  4   d  of large surface area is especially conveyed by means of radiation to the side screens  19   a ,  19   b  of large surface area to a considerable extent, from where the heat is radiated out to the colder atmosphere. As a result of that radiation, the expansion of the side screens  19   a ,  19   b  is less than that of the cylinder ends  4   c ,  4   d , which results in a reduction in the carding nip a ( FIG. 2   a ) and in the carding nip d ( FIG. 7   a ) that ranges from undesirable (in terms of the result of carding) to hazardous. The carding elements (card top bars  14 ) are mounted on the flexible bends  17   a ,  17   b  and the fixed carding elements  23 ′,  23 ″ are mounted on the extension bends, which are in turn fixed to the side screens  19   a ,  19   b . In the event of heating, the lifting of the flexible bends  17   a ,  17   b —and, as a result, of the clothings  18  of the card top bars  14  —increases less, compared to the expansion of the radius r 3  of the cylinder wall  4   e —and, as a result, of the clothing  4   a  of the cylinder  4  —, which results in narrowing of the carding nip a. The cylinder wall  4   e  and the cylinder ends  4   c ,  4   d  are made of steel, for example St 37, having a linear thermal expansion coefficient of 11.5×10 −6  [1/° K]. In order then to compensate for the relative differences in the expansion of the cylinder ends  4   c ,  4   d  and the cylinder wall  4   e , on the one hand, and the side screens  19   a ,  19   b  (as a result of impeded radiation into the atmosphere because of encasing of the cylinder  4  and free radiation into the atmosphere from the side screens), the rear parts  14   a  and carrying members  14   b  of the card top bars are made of carbon fibre reinforced plastics material (CFRP) whose thermal expansion coefficient has been negatively adjusted. By that means, even though the expansion of the cylinder  4  remains the same because of a lack of removal of heat as a result of encasing, the card top bars  14  undergo contraction. As a result, undesirable reduction in the carding nip a and d due to thermal influences is avoided. 
   In the embodiment of  FIG. 5 , three non-moving stationary carding elements  23   a ,  23   b ,  23   c  and non-clothed cylinder-encasing elements  25   a ,  25   b ,  25   c  are provided between the licker-in  3  and the card-top-deflecting roller  13   a . In accordance with  FIG. 7   a , the stationary carding elements  23  have a clothing  23 ′, which is located opposite the cylinder clothing  4   a . Reference letter d denotes the carding nip between the clothing  23 ′ and the cylinder clothing  4   a . The stationary carding elements  23 , by means of screws  26   a , and the cover elements  25  (by means of screws which are not shown) are mounted on an extension bend  27   a  (the extension bend  27   a  on only one side of the carding machine is shown in  FIG. 3 ), which is in turn fastened by means of screws  27   1  to  27   2  to the card screen  19   a  and  19   b  (only  19   a  is shown in  FIG. 5 ) on each side of the carding machine. The flexible bends  17   a ,  17   b  (only  17   a  is shown in  FIG. 5 ) are fastened to the side screens  19   a  and  19   b , respectively, by means of screws  29   1 ,  29   2  (see  FIG. 6 ). 
     FIGS. 6 and 7  show, as separate components, the flexible bend  17   a  and the extension bend  26   a , respectively. The flexible bend  17   a  is made, for example, of GGG 30 grey cast iron, and the extension bend is made, for example, of GG 20 grey cast iron. On the convexly curved periphery of the flexible bend there is fixed a coating  37  and on that of the extension bend  26   a  there is fixed a coating  38 , the two coatings  37 ,  39  being made of CFRP having positively adjusted thermal expansion coefficients. 
   The cylinder  4  is made, for example, of steel. In order to counteract, in use, the undesirable narrowing of the carding nips a ( FIG. 2 ) and d ( FIG. 7   a ), the flexible bends  17   a ,  17   b  and the extension bends  26 ,  26   b  are respectively provided with the coating  37  ( FIG. 6) and 38  ( FIG. 7 ) of carbon fibre reinforced plastics material (CFRP) whose thermal expansion coefficient has been positively adjusted. As a result, even though the expansion of the cylinder  4  is unchanged, the flexible bends  17   a ,  17   b  and extension bends  26   a ,  26   b  arranged to the sides of the cylinder  4  undergo expansion, as a result of which the card top bars  14  and stationary carding segments  23 , respectively, are lifted up so that the undesirable reduction in the carding nip a and d, respectively, is avoided. 
   The arrangement of the flexible bends  17   a ,  17   b  and extension bends  26   a ,  26   b  shown in  FIGS. 5 to 7  can advantageously be combined with the arrangement of the cylinder  4  shown in  FIGS. 3   a ,  3   b . In that combination, the flexible bends  17   a ,  17   b  and extension bends  26   a ,  26   b  are made at least sometimes of CFRP having a positively adjusted thermal expansion coefficient and the sheath  36  of the cylinder  4  (see  FIGS. 3   a ,  3   b ) is made of CFRP having a negatively adjusted thermal expansion coefficient. Where appropriate, CFRP having a thermal expansion coefficient of zero can also be selected, depending on the material of the cylinder  4 . By that means, as a result of suitable adjustment of the thermal expansion coefficients, a desired dimensional accuracy can be achieved and maintained as intended for the parts influencing the carding nip a and d in use when heat is generated. 
   In order to compensate for the relative differences in the expansion of the cylinder ends  4   c ,  4   d  and the cylinder wall  4   e , on the one hand, and the side screens  19   a ,  19   b  (as a result of impeded radiation into the atmosphere because of encasing of the cylinder  4  and free radiation into the atmosphere from the side screens), the sheath  36  is, in accordance with a further arrangement, made of carbon fibre reinforced plastics material (CFRP) whose thermal expansion coefficient has been negatively adjusted. By that means, expansion of the cylinder  4  because of a lack of removal of heat as a result of encasing is reduced or avoided. As a result, undesirable reduction in the carding nip a or d due to thermal influences is avoided. 
   Although the foregoing invention has been described in detail by way of illustration and example for purposes of understanding, it will be obvious that changes and modifications may be practised within the scope of the appended claims.
A carding machine has a number of rollers including a cylinder and having at least one clothed and/or unclothed machine element located opposite the cylinder at a spacing therefrom. The machine may have further elements influencing the carding nip. In order to make possible a carding nip between the cylinder and the clothed and/or unclothed counterpart element that remains constant or virtually constant when heat is generated, the parts influencing the carding nip are so construed that they have thermal expansion characteristics which are such that, when subjected to the heat acting on them in use, the carding nip remains substantially constant.