Abstract:
The invention relates to a reciprocating piston composed of ceramic material for a reciprocating-piston engine with crank drive, wherein the reciprocating piston is rigidly screwed to a piston rod by a screw, wherein between the reciprocating piston and the piston rod there is braced at least one disc composed of metallic material, wherein the screw is composed of a metallic material, wherein the coefficient of thermal expansion α piston  of the material of the reciprocating piston is lower than the coefficient of thermal expansion α screw  of the material of the screw, and the disc is an expansion compensation disc, wherein the coefficient of thermal expansion α Disc 1;2  of the material of the expansion compensation disc is greater than the coefficient of thermal expansion α screw  of the material of the screw, and to a reciprocating-piston engine having a reciprocating piston of said type, and to a cylinder of a reciprocating-piston engine having a cylinder of said type.

Description:
FIELD OF THE INVENTION 
     The present invention relates to a ceramic reciprocating piston for a reciprocating piston machine, in particular a reciprocating piston engine, having a crank mechanism, preferably a Scotch yoke mechanism, and having a piston rod rigidly connected to the reciprocating piston. The present invention also relates to a reciprocating piston machine, in particular a reciprocating piston engine, having a crank mechanism, preferably a Scotch yoke mechanism, and having such a ceramic reciprocating piston. 
     The invention also relates to a cylinder of a reciprocating piston machine, in particular a reciprocating piston engine, having a crank mechanism, preferably a Scotch yoke mechanism, having at least one ceramic cylinder bushing situated in a cylinder bore of the cylinder, and having a ceramic reciprocating piston that is guided so that it can reciprocate in the cylinder bushing. 
     BACKGROUND OF THE INVENTION 
     EP 0 197 449 B1 has disclosed a multi-part reciprocating piston for internal combustion engines, which in particular has a Scotch yoke mechanism and is rigidly connected to a piston rod. This piston includes a piston skirt that has a piston skirt base and is composed of a ceramic material, e.g. zirconium oxide, silicon nitride, or silicon carbide, in particular Si—SiC, and includes a piston base that has a head land and is likewise made of ceramic material and is provided with an annular groove for accommodating a split piston ring composed of a ceramic material. The piston base rests against the piston skirt base and the two main parts of the piston are radially fixed by means of a shared centering sleeve, likewise composed of ceramic material. The reciprocating piston also has a centering piece that is fixed on the piston rod with a snug fit and is composed of metal or of a metal alloy, with a base plate on which the piston skirt base rests and with an end cover that is made of the same material as the centering piece and rests against the piston base while extending radially to its head land. The end cover has a centering hub that is radially fixed relative to the centering piece, with an axial spacer gap between the two parts; the piston skirt base and the piston base are axially clamped between the end cover and the base plate by a screw connection associated with the piston rod. Because of the two-part embodiment, it is also possible to use piston rings composed of a ceramic material. This arrangement has proven useful. 
     DE 33 03 229 A1 has disclosed a ceramic internal combustion engine without piston lubrication, having a ceramic piston that travels in linear fashion in a ceramic cylinder; there is no contact between the ceramic piston and ceramic cylinder; instead, an annular gap is provided between them. 
     WO 00/25012 A1 has disclosed a carbon piston for an internal combustion engine. For example, piston rings composed of carbon can be used as piston rings for the piston. Also according to WO 00/25012 A1, the cylinder in which the carbon piston travels for example has a ceramic cylinder bushing, for example. The particular advantage of the carbon piston is that it has good limp-home properties. 
     The object of the present invention is to create a ceramic reciprocating piston for a reciprocating piston machine, in particular a reciprocating piston engine, having a crank mechanism, preferably a Scotch yoke mechanism, and having a piston rod rigidly connected to the reciprocating piston; a secure, permanent connection should be ensured, even during operation of the reciprocating piston machine. 
     Another object of the invention is to create a reciprocating piston machine equipped with such a reciprocating piston. 
     Another object of the invention is to create a cylinder of a reciprocating piston machine, in particular a reciprocating piston engine, having a crank mechanism, preferably a Scotch yoke mechanism, having at least one ceramic cylinder bushing situated in a cylinder bore of the cylinder, and having a ceramic reciprocating piston that is guided so that it can reciprocate in the cylinder bushing; a penetration of oil from the crank mechanism into the combustion chamber should be avoided and a long service life of the reciprocating piston machine should be ensured. 
     SUMMARY OF THE INVENTION 
     In certain embodiments, the invention is directed to a reciprocating piston composed of a ceramic material for a reciprocating piston machine, having a crank mechanism, preferably a Scotch yoke mechanism, in which the piston is rigidly connected to a piston rod by a screw, in particular a cap screw, and in which at least one disc composed of a metallic material is clamped between the reciprocating piston and the piston rod, characterized in that the screw is composed of a metallic material; the thermal expansion coefficient α piston  of the material of the reciprocating piston is lower than the thermal expansion coefficient α screw  of the material of the screw and the disc is an expansion compensation disc; and the thermal expansion coefficient α disc1;2  of the material of the expansion compensation disc is greater than the thermal expansion coefficient α screw  of the material of the screw. Two expansion compensation discs may be provided, with the reciprocating piston clamped between the expansion compensation discs. The thermal expansion coefficient α piston  may be 3.0·10 −6  to 6.5·10 −6  K −1 , or 4.5·10 −6  to 5.0·10 −6  K −1 . The thermal expansion coefficient α screw  may be 8.0·10 −6  to 10.0·10 −6  K −1 , or 9.0·10 −6  to 9.5·10 −6  K −1 . The thermal expansion coefficient α disc1  of the first expansion compensation disc may be 15.0·10 −6  to 19.0·10 −6  K −1 , or 16.5·10 −6  to 17.0·10 −6  K −1 . The thermal expansion coefficient α disc2  of the second expansion compensation disc may be 15.0·10 −6  to 19.0·10 −6  K −1 , or 16.5·10 −6  to 17.0·10 −6  K −1 . The reciprocating piston may be composed of a carbon material, in particular a graphite material. 
     In certain embodiments, the invention is directed to a reciprocating piston machine, in particular a reciprocating piston engine, in particular a reciprocating piston steam engine or reciprocating piston compressor, having a crank mechanism, in particular a Scotch yoke mechanism, characterized in that the reciprocating piston machine has a reciprocating piston as described above. In the reciprocating piston machine, the difference of the clamping force of the screw, in particular of the cap screw, at room temperature from the clamping force at the rated operating temperature of the reciprocating piston machine, which the reciprocating piston machine assumes during extended operation at the rated speed, may be &lt;0. The thermal expansion coefficient α screw  of the cap screw, the thermal expansion coefficients α disc2 disc1 ; α piston ; α piston rod ; α threaded bushing  of the parts clamped by the cap screw, the clamped lengths of these parts, and the clamping length of the cap screw are dimensioned so that the difference of the clamping force of the cap screw at room temperature from the clamping force at the rated operating temperature of the reciprocating piston machine, which the reciprocating piston machine assumes during extended operation at the rated speed, may be &lt;0. The clamping force of the screw, in particular of the cap screw, at room temperature may be less than the clamping force at the rated operating temperature of the reciprocating piston machine. 
     In certain embodiments, the invention is directed to a cylinder of a reciprocating piston machine, in particular of a reciprocating piston engine, having a crank mechanism, in particular a Scotch yoke mechanism, having at least one ceramic cylinder bushing situated in a cylinder bore of the cylinder, and having a ceramic reciprocating piston that is guided so that it can reciprocate in the cylinder bushing, in particular without piston lubrication, as described above, wherein the reciprocating piston is composed of a carbon material and the cylinder bushing is preferably composed of a silicon carbide material. 
     The invention further includes a reciprocating piston machine, in particular a reciprocating piston engine or reciprocating piston compressor, having a crank mechanism, in particular a Scotch yoke mechanism, wherein the reciprocating piston machine has a cylinder as described above. 
     The invention will be explained in detail below by way of example in conjunction with the drawings. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         FIG. 1 : is a longitudinal section through a reciprocating piston having a piston rod rigidly connected to the reciprocating piston according to a first embodiment of the invention. 
         FIG. 2 : is a longitudinal section through the reciprocating piston according to  FIG. 1 , without the piston rod and connecting means. 
         FIG. 3 : is a longitudinal section through a first expansion compensation disc. 
         FIG. 4 : is a longitudinal section through a second expansion compensation disc. 
         FIG. 5 : is a longitudinal section through a cap screw. 
         FIG. 6 : is a longitudinal section through a reciprocating piston, having a piston rod rigidly connected to the reciprocating piston according to another embodiment of the invention. 
         FIG. 7 : is a longitudinal section through a first piston part of the reciprocating piston according to  FIG. 6 . 
         FIG. 8 : is a longitudinal section through a second piston part of the reciprocating piston according to  FIG. 6 . 
         FIG. 9 : is a longitudinal section through a reciprocating piston, having a piston rod rigidly connected to the reciprocating piston according to another embodiment of the invention. 
         FIG. 10 : is a simplified perspective view of a part of the Scotch yoke mechanism in which one of the reciprocating pistons is depicted in exploded fashion. 
         FIG. 11 : is a simplified longitudinal section through the piston rod with a screw according to an alternative embodiment of the screw. 
         FIG. 12 : is a simplified longitudinal section through the piston rod with a screw according to another alternative embodiment of the screw. 
     
    
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS 
     The reciprocating piston  1  ( FIGS. 1, 6, and 9 ) has a piston base or piston base wall  2 , a piston shaft or piston skirt or piston casing  3 , and a piston axis  4 . 
     In the installed state, the reciprocating piston  1  is guided in an intrinsically known way so that it is able to reciprocate parallel to the piston axis  4  in a cylinder of a reciprocating piston machine. The reciprocating piston machine is preferably a reciprocating piston machine with a Scotch yoke mechanism  24  ( FIG. 4 ).  FIG. 10  schematically depicts part of the Scotch yoke mechanism  24  (without the crank mechanism) with a central Scotch yoke  25  and two piston rods  26 , which are each rigidly connected to a respective reciprocating piston  1  according to the invention at their one end and are each rigidly connected to the Scotch yoke  24  at their other end. The two piston rods  26  are also preferably each supported in an intrinsically known way so that they are able to reciprocate parallel to the piston axis  4  in a respective partition wall bearing of a partition wall of the housing of the reciprocating piston machine (not shown). As is known, the partition wall seals the housing part enclosing or accommodating the crank mechanism from the housing part accommodating the piston  1  and the cylinder. Depending on the type of reciprocating piston machine, the Scotch yoke mechanism  24  serves to convert the translatory, oscillating motion of the two synchronous pistons  1  into a rotation of a crank shaft (not shown) or the rotation of the crankshaft is converted into a translatory, oscillating motion of the two synchronous pistons  1 . In an intrinsically known way, the reciprocating piston machine also has a housing part for accommodating the crank mechanism and at least one cylinder with a cylinder bore for accommodating a piston  1  and a cylinder head (not shown) connected to the cylinder. According to a first aspect of the invention, the cylinder bore of the cylinder contains a cylinder bushing or cylinder liner  71  ( FIG. 9 ) composed of ceramic material. In this case, the cylinder bushing  71  is preferably supported in the cylinder bore in accordance with the applicant&#39;s German patent application DE 10 2010 054 060 “Cylinder of a Reciprocating-Piston Machine and Reciprocating-Piston Machine,” filed on Dec. 10, 2010, whose content is incorporated herein by reference. The cylinder according to the invention can furthermore be embodied as an individual cylinder, with several individual cylinders being suitably provided in a reciprocating piston machine. Alternatively, a plurality of cylinders according to the invention can be situated in a shared cylinder block. In this case, the individual cylinders can be arranged in a line or in the shape of a star. 
     In the installed state, the essentially disc-like piston base wall  2  has a base surface  5  at the cylinder head end and oriented toward the cylinder head, a base underside  6  oriented axially away from the latter, and a cylindrical base wall outer surface  7 . The base surface  5  is preferably planar and perpendicular to the piston axis  4 . In an intrinsically known way, the base surface of  5  closes one end of the combustion chamber or compression chamber in the reciprocating piston machine. The base wall outer surface  7  serves to guide the reciprocating piston  1  in the cylinder, in particular in the cylinder bushing, of the reciprocating piston machine. In addition, the bottom surface  5  has an annular, circumferential base edge  8  into which the base wall outer surface  7  transitions. In addition, a plurality of grooves  20  adjacent to one another in the axial direction are preferably provided in the base wall outer surface  7 , which in an intrinsically known way, serve as a labyrinth seal. 
     The piston wall  2  also has a cavity or recess  9 , particularly in the center, which extends from the base surface  5  into the piston base wall  2  in the direction of the piston axis  4 . The recess  9  has a recess bottom surface  10  and a recess circumference surface  11 . The recess bottom surface  10  is preferably planar and perpendicular to the piston axis  4 . The recess circumference surface  11  is preferably cylindrically embodied. The recess  9  also has a recess axis  12  that is preferably coaxial to the piston axis  4 . According to the invention, the recess  9  accommodates a first spacer disc or expansion compensation disc  13  whose function will be described in greater detail below. 
     The base underside  6  has a contact surface  14  that is arranged centrally with reference to the piston axis  4 . The contact surface  14  is in particular embodied as planar and perpendicular to the piston axis  4 . The contact surface  14  serves to contact a second spacer disc or expansion compensation disc  15  whose function will also be discussed in greater detail below. 
     The piston base wall  2  also has a continuous base opening  21  with a recess axis  22 . The recess axis  22  is preferably coaxial to the piston axis  4 . The base opening  21  extends continuously from the recess bottom surface  10  to the contact surface  14  through the piston base wall  2  and has a recess surface  23 . The base opening  21 , suitably viewed in the axial direction relative to the recess axis  22 , first has a conically tapering section, which is adjoined by a cylindrical section. 
     In the axial direction, the piston base wall  2  is adjoined by the piston casing  3 , which preferably starts with a first, in particular hollow, cylindrical or annular casing section  16 . The first annular casing section  16  is adjoined by a cylinder casing-segment-shaped second casing section  17 , which serves in a known way to control, in particular to open and close, the outlet slot. The piston casing  3  also has an in particular cylindrical casing outer surface  18 . The casing outer surface  18  adjoins the base wall outer surface  7  and transitions into it. The base wall outer surface  7  and the casing wall outer surface  18  thus constitute an outer, in particular cylindrical, piston outer surface or piston running surface  19  that serves to guide the reciprocating piston  1  in the cylinder bore of the cylinder. The embodiment of the piston casing  3  can vary and depends in an intrinsically known way on the respective requirements, for example the position of the inlet, outlet, and overflow openings in a reciprocating piston machine that function in accordance with the 2-stroke principle. In reciprocating piston machines that function in accordance with the 4-stroke principle, for example the cylinder casing-segment-shaped second casing section  17  is not provided since the control of inlet and outlet openings occurs in an intrinsically known way by means of the valves. 
     The reciprocating piston  1 , in particular the piston base wall  2  and the piston shaft  3 , which is preferably embodied of one piece with it, is composed, according to the invention, of ceramic or a ceramic material, in particular SiC or a carbon material, in particular a graphite material. Carbon materials are ceramics or ceramically fired inorganic materials that are chiefly composed of elemental carbon in one of the three naturally occurring carbon modifications. Among others, these include graphite materials (e.g. pure, impregnated, or in composite with metals). For the present invention, the graphite materials, in particular carbon graphite or electrographite, are preferably used for the reciprocating piston  1  due to their outstanding dry lubrication properties and limp-home properties. As is known, carbon graphite is produced as the first stage in the multistage manufacturing process that uses coking of the carbon-containing raw materials to produce artificial graphite materials as an essentially amorphous product. As is known, electrographite is produced through graphitization, a high-temperature treatment of carbon graphite in which the crystallinity increases and the material obtains its graphitic properties. The carbon material can be enriched with other materials, for example also with metals or metal alloys. 
     Preferably, the material of the reciprocating piston  1  has a thermal expansion coefficient α piston  of 3.0·10 −6  to 6.5·10 −6  K −1 , preferably 4.5·10 −6  to 5.0·10 −6 K −1 . 
     According to one aspect of the invention, the reciprocating piston  1 , which is composed of a carbon material, in particular a graphite material, is guided so that it is able to reciprocate in a direction parallel to the piston axis  4  in a ceramic cylinder bushing  71 . According to the invention, the cylinder bushing  71  is preferably composed of SiC (silicon carbide) or of Si 3 N 4  (silicon nitride). In particular, the cylinder bushing  71  is composed of Si-metal-infiltrated SiC (Si SiC) or SiSiC—C (carbon-containing silicon carbide) or of a composite of SiC and graphite, preferably SiC30, or a composite of Si 3 N 4  and graphite. The advantage of graphite-containing materials is that graphite functions as a lubricant. As a result, in the context of the present invention, preferably ceramic composite materials are used for the cylinder bushing  71 , which have particles composed of a solid, in particular mineral, lubricant, in particular are infiltrated with the lubricant; lubricants other than graphite are also a possibility, e.g. molybdenum sulfide MoS 2 . Moreover, the solid lubricant does not have to be infiltrated, but can also be mixed with the raw compound during manufacturing. 
     With this material combination selected according to the invention, no lubrication is required. The reciprocating piston  1  therefore runs dry in the cylinder bushing  71 . This is made possible by the material pairing according to the invention of the soft carbon material with a hard ceramic material. The graphite component of the carbon material ensures a sufficient solid lubrication and good limp-home properties. Since no oil for lubrication is present, this also means that no oil can get into the exhaust gases. The invention is particularly advantageous for reciprocating piston engines that run on biogas. This is because biogases often contain impurities, among other things a high sulfur content, causing sulfuric acid to be released during combustion. The toxic byproducts often attack the materials of the piston, which is not problematic in the reciprocating piston  1  according to the invention composed of the carbon material because the carbon material is resistant to corrosion by aggressive gases. Furthermore, the presence of the partition wall of the housing would require a separate piston lubrication, which would be expensive; the invention avoids this problem. 
     Furthermore, no piston ring is required since the thermal expansion coefficients of carbon and ceramic, in particular SiC, are relatively similar. 
     The diameter of the piston running surface  19  is also somewhat smaller than the inner diameter of the cylinder bore or diameter of the cylinder bushing running surface  71   a  of the cylinder bushing  71 —if one is provided—so that an annular gap is present between the piston running surface  19  and a running surface of the cylinder bore or cylinder bushing running surface  71   a . The annular gap must be dimensioned so that it ensures a sufficient seal of the combustion chamber or compression chamber. 
     As explained above, the reciprocating piston  1  according to the invention is also rigidly connected to the piston rod  26 . The attaching means provided for this includes a cap screw  27  and the first and second expansion compensation discs  13 ;  15 . 
     The cap screw  27  ( FIG. 5 ) is preferably a countersunk screw and has a screw head  28  and a screw shaft  29 . The screw head  28  preferably has a conical or tapered head support surface  30  that tapers toward the screw shaft  29 . The inclination of the head support surface  30  in this case is as slight as possible in order to achieve a good load distribution. Furthermore, the screw head  28  preferably has a head surface  72  with an engagement recess for a corresponding tool and a cylindrical outer head surface  73 . The head surface  72  transitions via a first circumferential edge  74  into the outer head surface  73  and the outer head surface  73  transitions via a second circumferential edge  75  into the head support surface  30 . The screw shaft  29 , starting from the screw head  28 , first has a conically tapering screw shaft section  31  whose outer surface is smooth, i.e. has no threads. The screw shaft section  31  is adjoined by a first cylindrical screw shaft section  32  whose outer surface is likewise smooth. The screw shaft section  32  is adjoined by a second cylindrical screw shaft section  33 , which has an external thread  34 . In order for elastic stretching of the screw to be able to be favorably absorb chronologically alternating changes in force and length that occur during operation, the outer diameter of the first cylindrical screw shaft section  32  is suitably smaller than the root diameter of the external thread  34 . 
     Furthermore, the cap screw  27  is composed of a metallic material, in particular titanium or a titanium alloy, or of steel, e.g. heat-resistant stainless steel, or of aluminum or an aluminum alloy. Preferably, the material of the cap screw  27  has a thermal expansion coefficient α screw  of 8.0·10 −6  to 10.0·10 −6  K −1 , preferably 9.0·10 −6  to 9.5·10 −6  K −1 . 
     The first expansion compensation disc  13  ( FIG. 3 ) is embodied in the form of an annular disc and has a first disc end surface  35 , a second disc end surface  36  oriented away from the latter, a disc circumference surface  37 , and a central disc opening  38  that has a disc opening axis  39  and extends from the first disc end surface  35  to the second disc end surface  36 . The two disc end surfaces  35 ;  36  are in particular planar and perpendicular to the disc opening axis  39 . The disc circumference surface  37  is preferably cylindrically embodied and transitions via a bevel  40  into the second disc end surface  36 . The disc opening  38  has an opening surface  41 , which, starting from the first disc end surface  35 , has a first tapered surface section  42  that narrows conically toward the second disc end surface  36  and is adjoined by a second cylindrical surface section  43 . The surface section  42  serves to support the head support section  30  of the cap screw  27 . Consequently, the inclination or pitch of the first surface section  42  corresponds to the inclination or pitch of the head support surface  30 . 
     Furthermore, the first expansion compensation disc  13  is preferably composed of a metallic material, e.g. a metal alloy, in particular steel, in particular heat-resistant stainless steel, or of aluminum or an aluminum alloy. Preferably, the material of the first expansion compensation disc  13  has a thermal expansion coefficient α disc1  of 15.0·10 −6  to 19.0·10 −6  K −1 , preferably 16.5·10 −6  to 17.0·10 −6  K −1 . 
     The second expansion compensation disc  15  ( FIG. 4 ) is likewise embodied in the form of an annular disc and has a first disc end surface  44 , a second disc end surface  45  oriented away from the latter, a disc circumference surface  46 , and a central disc opening  38  that has a disc opening axis  48  and extends from the first disc end surface  44  to the second disc end surface  45 . The two disc end surfaces  44 ;  45  are in particular planar and perpendicular to the disc opening axis  48 . The disc circumference surface  47  has an opening surface  52  that is preferably cylindrically embodied. The second expansion compensation disc  15  also preferably has an annular or tubular or hollow cylindrical collar  49  that adjoins the second disc end surface  45  and from it, protrudes essentially in a direction parallel to the disc opening axis  48 . The collar  49  has a cylindrical inner collar surface  50  and an outer collar surface  51 , which continuously adjoins the disc circumference surface  46 . In particular the outer collar surface  51  tapers in conical fashion, starting from the second disc end surface  45 . In particular, starting from the first disc end surface  44 , the disc circumference surface  46  first has a cylindrical section, which is adjoined by a conically tapering section. The latter serves to optimize the flow of air that sweeps along the base underside  6  during the oscillating motion of the reciprocating piston  1 . For this reason, the curvature of the base underside  6  is also flow-optimized. 
     The second expansion compensation disc  15  is preferably likewise composed of a metallic material, e.g. a metal alloy, in particular steel, in particular heat-resistant stainless steel, or of aluminum or an aluminum alloy. Preferably, the material of the second expansion compensation disc  15  has a thermal expansion coefficient α disc2  of 15.0·10 −6  to 19.0·10 −6  K −1 , preferably 16.5·10 −6  to 17.0·10 −6  K −1 . Preferably, the two expansion compensation discs  13 ;  15  are composed of the same material. They can, however, also be composed of different materials. 
     The piston rod  26  is preferably tubular or hollow cylindrical and has an in particular cylindrical inner rod surface  57  and an in particular cylindrical outer rod surface  58 . Furthermore, the piston rod  26 , at least at its broad end oriented toward the reciprocating piston  1 , has a threaded bushing  53  that is inserted into the piston rod  26  in form-locked fashion, in particular is welded or hard-soldered into it. The threaded bushing  53  has a central bushing opening extending through it, with an internal thread  56  that corresponds to the external thread  34  of the cap screw  27  ( FIGS. 6, 9 ). In addition, the threaded bushing  53  preferably has a bushing collar  54  with a planar end surface  55  ( FIGS. 6, 9 ). The threaded bushing is preferably composed of a metallic material, in particular high-strength steel, and the piston rod  26  is preferably likewise composed of a metallic material, in particular high-strength steel. 
     In the assembled state, i.e. during operation of the reciprocating piston machine, the reciprocating piston  1  is screw connected by means of the cap screw  27  to the piston rod  26  so that the reciprocating piston  1  and the piston rod  26  are detachably, but rigidly connected to each other. Preferably, two expansion compensation discs  13 ;  15  are clamped between the two parts to be connected to each other. 
     In particular, the first expansion compensation disc  13  is situated in the recess  9  so that the second disc end surface  36  rests against the recess bottom surface  10  and the disc opening  38  is aligned with the base opening  21  in a direction parallel to the piston axis  4 . The first disc end surface  35  preferably ends flush with the base surface  5 . In addition, the diameter of the recess circumference surface  11  is greater than the diameter of the disc circumference surface  37  so that a first annular gap is present between the recess circumference surface  11  and the disc circumference surface  37 . The first annular gap is necessary because the thermal expansion coefficient α disc1  of the first expansion compensation disc  13  is greater than the thermal expansion coefficient α piston  of the piston  1 . As a result, when exposed to heat, the first expansion compensation disc  13  expands more than the reciprocating piston  1 . The first annular gap at room temperature must be appropriately dimensioned in order to ensure that the first expansion compensation disc  13  does not expand to the point where it contacts the recess circumference surface  11  and presses against it, thus inducing stresses in the reciprocating piston  1 . 
     The second expansion compensation disc  15  rests with its first disc end surface  44  against the contact surface  14  of the reciprocating piston  1 ; the disc opening  47  is likewise aligned with the base opening  21  in a direction parallel to the piston axis  4 . The piston base wall  2  is thus situated and clamped between the first and second expansion compensation discs  13 ;  15 . 
     Furthermore, the rod end of the piston rod  26  oriented toward the reciprocating piston  1  is placed inside the disc collar  49  in a form-locked fashion; the end surface  55  of the bushing collar  54  rests against the second disc end surface  45  and the inner collar surface  50  of the disc collar  49  rests against the outer rod surface  58  so that the piston rod  26  is centered relative to the second expansion compensation disc  15 . 
     The cap screw  27  clamps the reciprocating piston  1 , the two expansion compensation discs  13 ;  15 , and the piston rod  26  to one another. For this purpose, the screw head  28  is placed inside the disc opening  38  of the first expansion compensation disc  13 ; the head support surface  30  of the screw head  28  rests against the conical surface section  42  of the disc opening  38 . The low inclination angle β produces a relatively large support surface between the head support surface  30  and the conical surface section  42  so that the force of the cap screw  27  is favorably distributed and excessive forces do not act on the recess bottom surface  10  of a ceramic reciprocating piston  1 . The screw shaft  29  extends with the first and second screw shaft sections  31 ;  32  through the rest of the disc opening  38  of the first expansion compensation disc  13 , the base opening  21 , and the disc opening  47  of the second expansion compensation disc  15 . In particular, the first screw shaft section  31  is situated inside the conical region of the second opening surface  23  of the base opening  21  and the second screw shaft region  32  is in particular situated inside the cylindrical region of the second opening surface  23  of the disc opening  47  of the second expansion compensation disc  15 . The outer diameter of the screw shaft sections  31 ;  32  are each smaller than the respective diameter of the surfaces  23 ;  43  encompassing them so that a second annular gap is present between the screw shaft sections  31 ;  32  and the surfaces  23 ;  43  encompassing them. The second annular gap in the region between the piston  1  and the screw shaft  29  is necessary because the thermal expansion coefficient α screw  of the cap screw  27  is greater than the thermal expansion coefficient α piston  of the piston  1 . As a result, when exposed to heat, the cap screw  27 , in particular the screw shaft  29 , expands more than the reciprocating piston  1 . The second annular gap at room temperature must be appropriately dimensioned in order to ensure that the screw shaft  29  does not expand to the point where it contacts the opening surface  23  of the base opening  21  and presses against it, thus inducing stresses in the reciprocating piston  1 . 
     The third screw shaft section  32  is screwed with its external thread  34  into the internal thread  56  of the threaded bushing  53  of the piston rod  26  so that the piston screw clamps the piston rod  26 , the two expansion compensation discs  13 ;  15 , and a reciprocating piston  1  to one another. 
     When connecting the reciprocating piston  1  to the piston rod  26 , the problem is that the manufacture and assembly of the individual parts as a rule occur at room temperature, but the parts are exposed to higher temperatures during operation of the reciprocating piston machine. Since the thermal expansion coefficient α screw  of the metallic cap screw  27 , due to the material of which is composed, is greater than the thermal expansion coefficient α piston  of the ceramic piston  1 , when exposed to heat during operation, in particular in the process of heating from room temperature  2  operating temperature, the cap screw  27 , particularly in a direction parallel to the piston axis  4 , expands more in terms of percentage and in actual distance than the reciprocating piston  1 . Without the expansion compensation discs  13 ;  15 , this would result in a significant reduction or even total loss of clamping force and a loosening of the screw connection. According to the invention, the thermal expansion coefficients α disc1  and α disc2  of the two expansion compensation discs  13 ;  15  are therefore greater than the thermal expansion coefficient α screw  of the cap screw  27  so that they expand more in terms of percentage and in actual distance than the cap screw  27 . The significantly smaller expansion of the reciprocating piston  1  in comparison to the cap screw  27  is thus balanced out or compensated for by the large expansions of the two expansion compensation discs  13 ;  15 . 
     The decisive factor here is the length changes of the clamped regions, each length being the span in the direction parallel to the piston axis  4 . According to the invention, an approximate design was arrived at by taking into consideration the length change ΔL piston  of the reciprocating piston  1  in the clamped region, i.e. the region between the recess bottom surface  10  and the contact surface  14 , whose length at room temperature is L 0,piston  ( FIG. 1 ), the length change ΔL disc1  of the first expansion compensation disc  13  in the clamped region, i.e. in the region between the first edge  74  of the screw head  28  or the head-end beginning of the head support surface  30  and the second disc end surface  36 , whose length at room temperature is L 0,disc1  ( FIG. 1 ), the length change ΔL disc2  of the second expansion compensation disc  13  in the clamped region, i.e. in the region between the first disc end surface  44  and the second disc end surface  45 , whose length at room temperature is L 0,disc2  ( FIG. 1 ), and the length change ΔL screw  of the cap screw  27  in the clamped region, whose length at room temperature is L 0,screw  ( FIG. 1 ). For the approximate design, the clamping region of the cap screw  27  was determined as the region between the first edge  74  of the screw head  28  and the beginning of the external thread  34  plus one fourth of the screw depth of the cap screw  27 . 
     For the length changes ΔL screw , ΔL disc1 , ΔL disc2 , and ΔL piston , of the clamped lengths L 0,disc1 , L 0,disc2 , L 0,piston , and of the clamping length L 0,screw , at room temperature when heated to the rated operating temperature, i.e. the operating temperature that the reciprocating piston machine reaches during continuous operation at the rated speed, the following equation applies: ΔL screw −(ΔL disc1 +ΔL disc2 +ΔL piston )=ΔL total , where preferably, 0.01 mm≦|ΔL total |≦0.03 mm. Preferably, ΔL total &lt;0. The rated speed is the speed at which the reciprocating piston engine generates the greatest possible output at full load, i.e. the rated output, or in a reciprocating piston compressor, the operating speed. 
     For the approximate design, average operating temperatures of the individual components were assumed. 
     For n discs, the following equation applies: ΔL discs =ΔL disc1 +ΔL disc2 + . . . +ΔL disc,n  and thus: ΔL screw −(ΔL discs +ΔL piston )=ΔL total . 
     In particular, the thermal expansion coefficients α screw , α disc1 , α disc2 , and α piston  and in particular the lengths L 0,screw , L 0,disc1 , L 0,disc2 , and L 0,piston  of the clamping region of the cap screw  27  and the clamped regions of the reciprocating piston  1  and of the two expansion compensation discs  13 ;  15  parallel to the piston axis  4  are dimensioned so that the clamping force is largely retained when the temperature is increased from room temperature to the rated operating temperature. 
     But α disc1  and α disc2  also must not be selected to be too high because although an excessive decrease in the clamping force would in fact result in a detachment of the connection, too excessive an increase in the clamping force would result in a fracturing of the reciprocating piston  1  due to the brittleness of the ceramic material. In establishing the design, it is thus necessary to take into account the fact that the operating temperatures of the individual parts  1 ;  13 ;  15 ;  27  can be different among other things due to their different distances from the base surface  5  and thus from the combustion chamber and furthermore, the individual parts  1 ;  13 ;  15 ;  27  can have different temperature distributions. Moreover, with an exact design, it is also necessary to take into account the length change of the cap screw  27  in the region of the entire thread  34  and the length changes of the clamped regions of the piston rod  26  and the threaded bushing  53  in the region of the thread  34 . In other words, it is necessary to determine the length changes of the individual parts at the respective operating temperatures and temperature distributions. 
     According to another embodiment of the invention ( FIG. 6 ), the reciprocating piston  1  is split into two parts in a direction parallel to the piston axis  4  and has a first piston part  1   a  oriented toward the combustion or compression chamber and a second piston part  1   b  oriented toward the crank mechanism, which are clamped to each other. In particular, the reciprocating piston  1  is divided in the vicinity of the piston base wall  2 . A parting plane  58  is in particular perpendicular to the piston axis  4 . In addition, the parting plane  58  is situated between the base surface  5  and the base underside  6 . As a result, the reciprocating piston  1  has a first piston base wall part  2   a  and a second piston base wall part  2   b . In particular, the first piston part  1   a  constitutes the first piston base wall part  2   a  and the second piston part  1   b  has the second piston base wall part  2   b . The first piston part  1   a  or first piston base wall part  2   a  has the base surface  5  and oriented axially away from this, a first, in particular planar, parting surface  59  and preferably, the grooves  20 . The first parting surface  59  transitions via a first continuous circumferential edge  64  into the base wall outer surface  7  of the first piston base wall part  2   a . In addition, the first piston base wall part  2   a  has a first part or opening section  60  of the base opening  21 , which extends through from the base surface  50  to the parting surface  59 . The second piston part  1   b  has the base underside  6  and oriented axially away from this, a second, in particular planar, parting surface  61  and the piston shaft  3 . The second parting surface  61  transitions via a second continuous circumference edge  65  into the base wall outer surface  7  of the second piston base wall part  2   b . The second piston base wall part  2   b  also has a second part or opening section  62  of the base opening  21 , which extends from the base underside  6  to the second parting surface  61 . The two opening sections  60 ;  62  are flush with each other in a direction parallel to the piston axis  4  and form the base opening  21 . The two opening sections  60 ;  62  here preferably have the same diameter so that the base opening  21  is embodied as continuously cylindrical. In addition, a centering sleeve  63  is suitably provided for centering the two piston parts  1   a ;  1   b  and two piston base wall parts  2   a ;  2   b , respectively, relative to each other. The centering sleeve  63  is situated inside the base opening  21 , i.e. inside the two openings  60 ;  62 . The outer diameter of the centering sleeve  63  corresponds to the diameter of the opening surface  23  of the base opening  21 . The inner surface of the centering sleeve  63 , preferably in the axial direction relative to the opening axis  22 , first has a conically tapering section, which is then adjoined by a cylindrical section. In addition, the diameters of the inner surface are dimensioned so that the inner surface is spaced apart from the first and second screw shaft sections  31 ;  32 . The room-temperature length of the centering sleeve  63  in the axial direction relative to the piston axis  4  corresponds in particular to the length of the base opening  21  in the axial direction relative to the piston axis  4 . Since the outer diameter of the centering sleeve  63  is smaller than the diameter of the second surface section  43 , the centering sleeve  63  when heated is free to expand in the axial direction toward the base surface  5 . In addition, the centering sleeve  63  preferably is composed of a metallic material, in particular titanium or a titanium alloy. 
     The two piston parts  1   a ;  1   b , in particular the two piston base wall parts  2   a ;  2   b , are likewise clamped to each other by means of the cap screw  27 . In this case, a rotation-preventing element such as an alignment pin (not shown) can also be provided in order to prevent the two piston parts  1   a ;  1   b  from rotating relative to each other. Since according to the invention, the clamping force is retained or changes only slightly, even at operating temperature, the clamping force is sufficient to prevent a rotation of the two piston parts  1   a ;  1   b  relative to each other and a rotation-preventing element is not absolutely required. 
     The advantage of the split embodiment is that the two circumferential edges  64 ,  65  constitute a blow-by prevention without requiring a piston ring. In addition, in the event of damage to the base surface  5 , it is possible to replace only the first piston part  1 , which reduces costs. 
     According to another embodiment ( FIG. 9 ), the piston  1  is likewise split in a fashion analogous to the preceding embodiment. In addition, the first piston base wall part  2   a  has a circumferential stepped shoulder  66 , which, starting from the first parting plane  59 , extends into the first piston base wall part  2   a  in both the axial and radial direction with regard to the piston axis  4 . The stepped shoulder  66  is thus embodied as stepped radially inward and preferably has a first planar step surface  67  extending perpendicular to the piston axis  4  and a second cylindrical step surface  68  extending perpendicular to the first step surface  67 . When assembled, the first and second step surfaces  67 ;  68  and a radially outer subregion of the second parting surface  61  form a circumferential piston ring groove  69  for accommodating a piston ring  70 . The piston ring  70  is preferably composed of a ceramic material, in particular a carbon material. Particularly for piston rings composed of ceramic, this embodiment with the two-part split piston  1  is particularly advantageous because their elasticity is often insufficient to allow them to be mounted over the piston  1  from the outside. 
     The advantage of the invention on the one hand is that through a deliberate material selection, arrangement, and dimensioning of the expansion compensation discs ensures a permanent connection of the reciprocating piston  1  to the piston rod  26 , even during operation of the reciprocating piston machine. The connection according to the invention compensates for the different thermal expansions of the reciprocating piston  1  and the cap screw  27 . It prevents a loosening of the connection. It also prevents initially exerted clamping force from fracturing the reciprocating piston due to the brittleness of the ceramic material. This is because excessive tightening of the cap screw  27  during the assembly, which takes place at room temperature, is not necessary in order to attain the optimal clamping force during operation. This ensures that the thermal expansion coefficient α screw  of the cap screw  27 , the thermal expansion coefficients α disc2 disc1 ; α piston ; α piston rod ; α threaded bushing  of the parts  1 ;  13 ;  15 ;  26 ;  53  clamped by means of the cap screw  27 , in particular the expansion compensation discs  13 ;  15 , the clamped lengths of these parts  1 ;  13 ;  15 ;  26 ;  53 , and the clamping length of the cap screw  27  are dimensioned so that the difference of the clamping force of the cap screw  27  at room temperature from the clamping force at the rated operating temperature of the reciprocating piston machine, which the reciprocating piston machine assumes during extended operation at the rated speed, is &lt;0. 
     The scope of the invention naturally also includes a solid embodiment of the piston rod. In this case, the internal thread required for the screw connection is provided directly in the piston rod at the end of the piston rod. 
     The scope of the invention also includes embodiments in which the two piston base wall parts  2   a ;  2   b  are not split along a planar parting plane, but stead, the parting surfaces  59 ;  61  are contoured and embodied correspondingly to each other. In this case, the centering sleeve  63  could be eliminated. 
     A screw is a cylindrical pin or stud on which a thread is provided. In screws with heads (“cap screws”), the annular surface under the head serves as an axial stop and the threaded pin constitutes the screw shaft. In the context of the invention, it is not absolutely necessary to use a cap screw  27 . Instead, it is also possible to use a screw without a screw head that only has a threaded pin or threaded stud  76  with an external thread, particularly in combination with a nut  77 . The metallic nut  77  and the metallic threaded pin  76  in this case are preferably composed of the same material, particularly titanium or a titanium alloy, analogous to the cap screw  27 . In this embodiment, the threaded pin  76  is screwed into the internal thread  56  of the threaded bushing  53  at one end and at the other end, in lieu of the screw head, the nut  77  is screwed on (not shown) so that the individual parts can be clamped to one another. 
     According to an alternative embodiment ( FIG. 11 ), the threaded pin  76  is embodied as thickened or widened at one end, its end oriented toward the piston rod  26 , and at one end, has a widened, in particular fully cylindrical, end region  78 . The end region  78  is preferably embodied of one piece with the threaded pin  76 . The end of the piston rod  26  oriented toward the piston  1  is equipped with an annular opening in the center; the base wall  79  closes the hollow, cylindrical piston rod  26 . The threaded pin  76  is inserted into the piston rod  26  from the rod end oriented away from the piston  1 ; the widened end region  78  is positioned in the piston rod  26  in a form-locked fashion and rests with an annular end surface  80  oriented toward the piston  1  against a first inner base wall inner surface  81  of the base wall  79 . The rest of the threaded pin  76  protrudes through the annular opening of the base wall  79  out of the piston rod  26  and extends analogously to the screw shaft  28  through the two expansion compensation discs  13 ;  15  and the piston  1  (not shown). The two expansion compensation discs  13 ;  15  and the piston  1  are clamped to the piston rod  26  by screwing the nut  77  onto the other end of the threaded pin  76 . In this case, a second outer base wall inner surface  82  of the base wall  79  rests against the second disc end surface  45 . 
     In lieu of the thickened end region  78 , the threaded pin  76  can also be solidly connected to the rod end of the piston rod  26  oriented toward the piston  1 , e.g. can be formed onto it ( FIG. 12 ). The piston rod  26  is then preferably embodied as solid. 
     When the threaded pin  76  is used as a screw, the in particular rough calculation of the length changes must be correspondingly adapted. Depending on the circumstances, for example, the length change of the nut  77  must be taken into account. 
     The arrangement according to the invention is also suitable for use for both reciprocating piston machines that function in accordance with the 2-stroke principle and those that function in accordance with the 4-stroke principle, in particular reciprocating piston engines. Moreover, it is suitable not only for reciprocating piston machines with a Scotch yoke mechanism, but also for any kind of reciprocating piston machine in which the piston rod is rigidly connected to the piston and in particular, is guided in linear fashion, for example crosshead engines or engines with hypocycloidal linear guidance. The invention is naturally not limited to reciprocating piston engines and reciprocating piston internal combustion engines, but can also be used in reciprocating piston compressors such as oxygen compressors or reciprocating piston pumps or reciprocating piston steam engines such as a Murray steam engine.