Abstract:
A Continuous Ambulatory Haemofiltration device consisting of an outer casing, multifunction pump, haemofilter, reversed osmosis filter, power source, drainage bag, blood lines and fluid lines. Haemofiltrate from the haemolfilter is moved to a reversed osmosis filter. Ultrafiltrate fluid from the reversed osmosis filter flows to an out-flow tube of the haemofilter venous line through a specific fluid line. The exit of the reversed osmosis filter is connected to a drainage bag. A multifunction pump moves blood from a permanent jugular catheter to the haemofilter, and fluids between the haemofilter, reversed osmosis filter, venous line and drainage bag. An electrode is placed at the in-flow tube of the haemofilter to measure incoming blood osmolality. An electrode is connected to a microprocessor that is further connected to a computer-controlled valve at an out-flow line of the reversed osmosis filter. A microprocessor is connected with a memory card.

Description:
CROSS-REFERENCE TO RELATED APPLICATION 
       [0001]    This application is a national stage application and claims the benefit of the priority filing date in PCT/EP2009/009141 referenced in WIPO Publication WO 2011/072707 A1. The earliest priority date claimed is Dec. 18, 2009. 
     
    
     FEDERALLY SPONSORED RESEARCH 
       [0002]    Not Applicable 
       SEQUENCE LISTING OR PROGRAM 
       [0003]    Not Applicable 
       STATEMENT REGARDING COPYRIGHTED MATERIAL 
       [0004]    Portions of the disclosure of this patent document contain material that is subject to copyright protection. The copyright owner has no objection to the facsimile reproduction by anyone of the patent document or the patent disclosure as it appears in the Patent and Trademark Office file or records, but otherwise reserves all copyright rights whatsoever. 
       BACKGROUND 
       [0005]    The invention relates to a transmission as generically defined by the preamble to claim  1  or by the preamble to claim  2 . 
         [0006]    Transmissions of the aforementioned type are described for instance in international patent disclosure WO 95/22017. Such a transmission has a hollow-cylindrical main body with end faces that is provided with an internal toothing and has a rotary axis. In the main body, a driven input member and an output member are supported rotatably about the rotary axis. The output member includes two spaced-apart rotary bodies, with a circular cross section transversely to the rotary axis. The rotary axis is perpendicular to the two rotary bodies. The rotary bodies can be or are connected fixedly to one another. At least one gear wheel that meshes with the inner gear wheel, as well as means for converting planetary motions of the gear wheel into rotary motions of the output member (also called “converting means” or “conversion means”), are disposed between the rotary bodies. These converting means or conversion means for converting planetary motions of the gear wheel into rotary motions of the output member have a central opening through which the input member is passed, and four arms facing one another in pairs and uniformly distributed in the form of a cross around the central opening. The input member is supported on both sides in the rotary bodies of the output member, and the output member is in turn supported on both sides in the hollow-cylindrical main body. 
         [0007]    Such transmissions have a disadvantage in that the conversion means, which in simplified terms are in the form of a cross, can only be manufactured after major technical effort and expense. Moreover, the force distribution inside the cross is unfavorable during torque transmission to the output member, which occurs simultaneously with the conversion of the planetary motion into rotary motion. This is especially so with regard to the incident forces because this is an “open” system. 
         [0008]    According to international patent disclosure WO 2007/135540 A2, transmissions with adjustable torque transmission during operation are known. For that purpose, each of the transmissions has at least one fixed wheel split into two axially spaced parts, around which a belt is laid whose length is greater than the circumference of the wheel. A satellite wheel is disposed between the two parts of the fixed wheel. The satellite wheel has a different diameter from the fixed wheel. One input member and one output member are disposed coaxially to a rotary axis. The input member has at least one portion which has an adjustable eccentricity and on which at least one satellite wheel is disposed. Rotation of the input member causes the satellite wheel to roll on the inside face of the belt. With increasing eccentricity, the friction between the satellite wheel and the belt increases, so that a higher torque is transmitted. The conversion of the planetary motion of the satellite wheel into a rotary motion of the output member happens in various ways, depending on the design of the transmission:
       If only one satellite wheel is provided, the output member comprises a rotary body disposed on one side of the satellite wheel. In that case, an annular conversion means can be provided between the satellite wheel and the output member. Both end faces of the ring then each have two guide means with center axes. The center axes of the guide means on one end face extend perpendicular to an axial plane, while the center axes of the guide means on the other end face extend parallel to the axial plane.   If two or more satellite wheels are provided, the output member comprises two rotary bodies, connected to one another by means of spacers and spaced axially apart from one another in the direction of the rotary axis. In that case, the satellite wheels move phase-offset by 180°, and the conversion of the planetary motions into a rotary motion of the output member is effected directly via the spacers. To that end, the spacers are guided through eccentric openings in the satellite wheels. Each of the spacers, in every opening it passes through, has constant linear contact, in every configuration, with the respective satellite wheel.       
 
         [0011]    This last manner of converting planetary motions into rotary motions is generally known, for instance, from patent disclosures U.S. Pat. No. 1,767,866, EP 0 474 897 A1, EP 1 816 374 A1, U.S. Pat. No. 3,129,611, and PL 169808, as well as in transmissions which, as described at the outset, have an output member which comprises two rotary bodies, connected to one another by means of spacers and spaced apart axially from one another in the direction of the rotary axis, and at least one gear wheel, disposed between the rotary bodies, which meshes with an internal toothing and executes planetary motions. It is also known in transmissions that have an output member that comprises only one rotary body with pins disposed eccentrically on it, which pins extend in the axial direction of the rotary axis and protrude into eccentric openings in one or more gear wheels, offset axially from the rotary body, that mesh with an internal toothing and execute planetary motions. Each spacer or pin, in every opening it passes through, always and in every configuration has constant linear contact with the respective gear wheel. 
         [0012]    From French patent disclosure FR 797 130 A, a transmission with a variable gear ratio and a transmission with a fixed gear ratio are known. Each of the two transmissions has a housing with a rotary axis, and with an input and output member, both disposed in the housing rotatably about the rotary axis. The input member has an eccentric portion on which a gear wheel is disposed. The gear wheel meshes with an internal toothing disposed in the housing. Rotation of the input member causes the gear wheel to execute a planetary motion. The output member comprises a rotary body disposed on one side of the gear wheel. Conversion means for converting planetary motions into rotary motions of the output member are disposed between the rotary body of the output member and the gear wheel. The conversion means comprise a ring. Each of the two end faces of the ring has two guide means with center axes. The center axes of the guide means of one face end extend perpendicular to an axial plane, while the center axes of the guide means of the other face end extend parallel to the axial plane. A gear ring with an external toothing and an internal toothing is disposed, rotatably supported about the rotary axis in the housing of the transmission that has the variable gear ratio. A worm, which meshes with the external toothing of the gear ring, extends into the housing. The worm can be driven at a variable speed by an electric motor, and the gear ratio between the input member and the output member varies with the speed. 
         [0013]    From Japanese patent disclosure JP 1 143 171, transmissions with a variable gear ratio are known. The transmissions have a housing with a rotary axis and an input and output member, both of which are disposed rotatably about the rotary axis in the housing. The input member has at least one eccentric portion, on which at least one gear wheel is disposed. The gear wheel meshes with an internal toothing. The internal toothing is located in a rotatably supported bell disposed in the housing. The bell can be driven at a variable speed. With the speed, the gear ratio also varies. The output member comprise a rotary body disposed on one side of the at least one gear wheel. Both end faces of the ring each have two guide means with center axes. The center axes of the guide means of one face end extend perpendicular to an axial plane, while the center axes of the guide means of the other face end extend parallel to the axial plane. In a transmission with two gear wheels that, upon a 180° rotation of the input member execute phase-offset planetary motions, the gear wheels have eccentric openings. Pins extending in the axial direction of the rotary axis pass through these openings and are disposed eccentrically on the rotary body that is disposed on one side of the gear wheels. In each eccentric opening that it passes through, and in every configuration, each pin always has linear contact with the respective gear wheel. 
         [0014]    In the known transmissions, there is a disadvantageous in that their construction allows for only a limited load, because
       they have only one rotary body as an output member, to which a torque is transmitted unilaterally with or without the aid of a conversion means for converting planetary motions of the gear wheel into rotary motions of the output member;   while they have two rotary bodies connected to one another and are axially spaced apart from one another by spacers, the torque transmission, with simultaneous conversion of the planetary motion of the wheels disposed between the rotary bodies into a rotary motion of the output member, is still effected directly by the wheels via the spacers; or   the conversion means in the form of a cross are provided between the gear wheel and the output member, and these means form an open system with regard to the forces that occur when a torque is transmitted.       
 
         [0018]    With the above prior art as the point of departure, it is the object of the invention to provide a remedy for these disadvantages. 
         [0019]    The stated object is attained by the features of claim  1  and the features of claim  2 . 
       SUMMARY 
       [0020]    A transmission having the features of claim  1  includes a hollow-cylindrical main body with end faces that has an internal toothing and a rotary axis, in which main body a driven input member and an output member are rotatably supported. The output member includes two rotary bodies with spacers, the rotary bodies being connectable or connected non-rotatably to one another and having a circular cross section transversely to the rotary axis. Between the rotary bodies, at least one gear wheel and at least one means for converting planetary motions of the gear wheel into rotary motions of the output member are disposed. According to the invention, it is provided that the converting means or conversion means or means for converting planetary motions of the gear wheel into rotary motions of the output member, called simply means for short, has the form of a ring with a central opening. At least two guide means are disposed on each of the two end faces of at least one means. The guide means, each disposed on one end face, are disposed relative to opposite sides of the central opening such that their center axes preferably coincide or preferably form a common center axis. Moreover, the center axes of the guide means on one end face extend perpendicular to an axial plane, while the center axes of the guide means of the other end face extend parallel to that axial plane. In other words, the center axes of the guide means of one end face extend perpendicular to the center axes of the guide means of the other end face. At the same time, the center axes of all the guide means extend perpendicular to the rotary axis, and more precisely perpendicular to planes in each of which the rotary axis is located or which are formed by the rotary axis. That is, an annular plane formed by the ring and located parallel to the end faces extends perpendicular to the rotary axis, and the center axes of the guide means extend parallel to that annular plane. The ring, moreover, has continuous, axially oriented openings, which spacers (preferably spacers connecting the rotary bodies of the output member non-rotatably to one another) pass through without contact. 
         [0021]    Accordingly, a transmission having the features of claim  2  includes a hollow-cylindrical main body with end faces having an internal toothing and a rotary axis. In the main body, a driven input member and an output member are rotatably supported. The input member has an eccentric portion, on which a gear wheel is disposed. The gear wheel meshes with the internal toothing. Rotation of the input member causes the gear wheel to execute a planetary motion. The transmission furthermore includes means for converting planetary motions of the gear wheel into rotary motions of the output member. The means are embodied in the form of a ring. Both end faces of the ring each have at least two guide means with center axes. The center axes of the guide means of one end face extend perpendicular to an axial plane, while the center axes of the guide means of the other end face extend parallel to the axial plane. The output member includes two rotary bodies connected non-rotatably to one another. The rotary bodies have a circular cross section transversely to the rotary axis. The rotary bodies are spaced apart from one another in the axial direction of the rotary axis and are connected to one another by spacers. Between the rotary bodies the at least one gear wheel and the at least one means for converting planetary motions of the gear wheel into rotary motions of the output member are disposed. The ring of the means for converting planetary motions of the gear wheel into rotary motions of the output member has continuous, axially oriented openings. Spacers pass through these openings without contacting them. 
         [0022]    The invention is realized in cases relating to a transmission in which the means for converting planetary motions of the gear wheel into rotary motions of the output member (converting means or conversion means) is, or are, in the form of a ring; it is therefore a closed system in regards to the incident forces, in which the guide means are positioned on the face ends. The guide means can be embodied in the form of raised areas or recesses, which are operatively connected to corresponding parts of the rotary bodies. Annular means are easier to manufacture than crosses and have greater strength. In addition, because of their more homogeneous tension distribution, annular means have improved force distribution in the material employed. Thus, at the same cost for material, or in other words using the same material and the same weight, they can bear heavier loads than a cross employed in the prior art. Moreover, at the same load-bearing capacity, in comparison to such a cross, they can either be produced from a less-expensive material, which may also be simpler to process and manufacture, or they are lighter. 
         [0023]    Further expedient and advantageous embodiments of the invention will become apparent from the dependent claims. 
     
    
     
       DRAWINGS 
         [0024]    One exemplary embodiment of the invention is shown schematically in the drawings and will be described in detail hereinafter. In the drawings: 
           [0025]      FIG. 1  shows a transmission in an exploded view; 
           [0026]      FIG. 2  shows the transmission of  FIG. 1  in the assembled state; 
           [0027]      FIG. 3  is a section taken along the line A-A in  FIG. 2 ; 
           [0028]      FIG. 4  is a section taken along the line B-B in  FIG. 2 ; 
           [0029]      FIG. 5  shows the first rotary body in perspective; 
           [0030]      FIG. 6  shows a means in perspective; 
           [0031]      FIG. 7  shows a gear wheel in perspective; and 
           [0032]      FIG. 8  shows the second rotary body in perspective. 
       
    
    
     LIST OF REFERENCE NUMERALS 
       [0000]    
       
           3  Bearing body 
           4  Continuous opening at input member 
           10  Input member 
           12  Roller element 
           17  Eccentric portion 
           30  Gear wheel 
           30   a  Axis of the gear wheel 
           30   b  Linear guide on the gear wheel 
           31  Inner running surface 
           32  Opening 
           33  External toothing 
           34   a,    34   b  Guideways of the linear guide on the gear wheel 
           35   a,    35   b  Rasied areas on the gear wheel 
           40  Main body 
           40   a  Rotary axis 
           40   b  Plane 
           41  Internal toothing on the main body 
           41   a  Axial grooves on the inner circumference of the main body 
           41   b  Needle-like roller bodies, disposed in the axial slots 
           42   a  Running surface 
           43  Bearing 
           49  End face 
           50 ,  50 ′ Rotary body 
           50   b  Linear guide 
           51 ,  51 ′ Central opening 
           52  Spacer 
           53 ,  53 ′ Axial recesses in spacers 
           54   a,    54   b  Guideways 
           55   a,    55   b  Raised areas 
           59  Threaded recesses 
           60  Connecting element 
           70  Conversion element 
           71  Central opening in conversion element 
           74 - 1  Guide means 
           74 - 2  Guide means 
           74 - 3  Guide means 
           74 - 4  Guide means 
           74   a,    74   b  Guideways 
           75   a,    75   b  Guideways 
           77 -X Center axis 
           77 -Y Center axis 
           78  Axially oriented openings 
           80 ,  90  Roller elements 
         e Eccentricity 
       
     
       DETAILED DESCRIPTION 
       [0077]    The transmissions shown in their entirety or in part in  FIGS. 1-8  all comprise a hollow-cylindrical main body  40  with face ends  49  which has an internal toothing  41  and a rotary axis  40   a  and in which a driven input member  10  and an output member are rotatably supported. The output member includes two rotary bodies  50 ,  50 ′. The rotary bodies  50 ,  50 ′ are embodied essentially in disk-like fashion. The disk-like parts of the rotary bodies  50 ,  50 ′ are spaced apart from one another by spacers  52 . The rotary bodies  50 ,  50 ′ are connectable or connected fixedly to one another. The rotary bodies  50 ,  50 ′ have a circular cross section transversely to the rotary axis  40   a.  Two gear wheels  30  are disposed between the rotary bodies  50 ,  50 ′. The gear wheels  30 , with their external toothing  33 , mesh with the internal toothing  41  of the main body  40 . Between the rotary bodies  50 ,  50 ′, there are also means for converting planetary motions of the gear wheels  30  into rotary motions of the output member. The means are embodied in the form of conversion elements  70 . In addition, an annular retaining body, not shown, can be connected fixedly to the end face  49 . Via roller elements, the rotary body  50  is braced in both the axial and radial directions directly on the main body  40  and on the retaining body that is disposed on the face end  49 . 
         [0078]    The functional layout of the moving parts disposed between the rotary body  50 ,  50 ′ in the main body  40  is identical in all the exemplary embodiments shown in the drawings. An input member  10  in the form of an input shaft has two eccentric portions  17 , which are offset from one another by 180°. The eccentric portions  17  are offset from the rotary axis  40   a  by an eccentricity e. One gear wheel  30  is rotatably supported on each of the eccentric portions  17 . The eccentricity e is thus equivalent to the spacing between the axis  30   a  of a gear wheel  30  and the rotary axis  40   a  of the main body  40 . To reduce friction losses, roller elements  12  that each roll on the outer circumference of the eccentric portions  17  are disposed between the eccentric portions  17  and the gear wheels  30 . To that end, tracks for the roller elements  12  are embodied on the circumference of the eccentric portions  17  and act as bearing bodies for the gear wheels  30 . The gear wheels  30  each have an external toothing  33  and central openings with inner running surfaces  31  for the roller bodies  12 . 
         [0079]    The gear wheels  30  each have a plurality of continuous axial openings  32 , offset radially from the central opening that has an inner running surface  31 , which are all distributed uniformly about the axes  30   a  of the gear wheels  30 . The axes  30   a  of the gear wheels  30  extend parallel to the rotary axis  40   a  of the input member  10  and of an output member formed by two rotary bodies  50 ,  50 ′. The rotary axis  40   a  is, at the same time, the axis of symmetry of the main body  40 . The input member  10  can be connected, for instance by means of a spring, to a motor shaft of a drive motor. The drive motor can be connected, for instance, by means of a cap (not shown) and screws, to the main body  40  that has the internal toothing  41  and is embodied as an internal geared wheel. The drive motor can be disposed, for instance, on the side of the transmission facing away from the rotary body  50  supported in the main body  40 . That side then forms the driving end of the transmission, while conversely the rotary body  50  supported in the main body  40  forms the driven end of the transmission. 
         [0080]    The gear wheels  30  are disposed in the middle between the two rotary bodies  50 ,  50 ′ embodied with a circular outer contour or circular cross section transverse to the rotary axis  40   a,  and these rotary bodies are disconnectably connected to one another by connecting elements  60  and jointly form the output member of the transmission. The spacers  52 , which have openings and threaded recesses for receiving the connecting elements  60 , are disposed on the rotary body  50 . The spacers  52  pass without contact through the openings  32  in the gear wheels  30 , so that the rotary bodies  50 ,  50 ′ can be connected fixedly to one another all the way through the gear wheels  30 . The output member formed by the two rotary bodies  50 ,  50 ′ that are connected to one another is supported rotatably about the rotary axis  40   a  relative to the main body  40  having the internal toothing  41 . 
         [0081]    The internal toothing  41  of the main body  40  meshes with the external toothing of the gear wheels  30 . The axes of the gear wheels  30  are disposed parallel to the rotary axis  40   a  of the main body  40 , but offset by the eccentricity e. The rotary bodies  50 ,  50 ′ are provided with guideways  54   a,    54   b,  which define a linear guide  50   b.  The linear guide  50   b  is oriented transversely to the rotary axis  40   a  of the rotary bodies  50 ,  50 ′. Each gear wheel  30  is provided with guideways  34   a,    34   b,  which define a linear guide  30   b,  and this linear guide  30   b  is oriented transversely to the axis  30   a  of the gear wheel  30 . On both sides of the transmission, a conversion element  70  embodied as a ring is disposed between the respective rotary body  50  and  50 ′ and the gear wheel  30 . In two directions orthogonal to one another, the conversion element  70  has guide faces  74 - 1 ,  74 - 2  and  74 - 3 ,  74 - 4 , respectively, which correspond to the linear guides  50   b  and  30   b  of the respective rotary body  50 ,  50 ′ and gear wheel  30  in such a way that relative to the respective rotary body  50 ,  50 ′ on the one hand and the respective gear wheel  30  on the other, the conversion element  70  is disposed displaceably in two directions that are orthogonal to one another. One linear guide  50   b  is embodied on the rotary body  50  or  50 ′, while the conversion element is disposed displaceably in the other direction in the linear guide  30   b  on the gear wheel  30 . 
         [0082]    The two rotary bodies  50 ,  50 ′ and the conversion elements  70  have central openings  51 ,  51 ′ and  71 , respectively. The input member  10  is supported on both of its ends in the central openings  51 ,  51 ′ of the rotary bodies  50 ,  50 ′. The central openings  50 ,  51 ′ form tracks on their inner faces for bearing bodies  3 . By means of the bearing bodies  3 , the ends of the input member  10  are supported in the central openings  51 ,  51 ′ of the rotary bodies  50 ,  50 ′. The input member  10  passes without contact through the central opening  71  of the conversion element  70 . The inside diameter of the central opening  71  is greater, by at least 2e, than the outside diameter of the portion of the input member  10  that passes through the central opening  71 . The guideways  54   a  and  54   b,  with which each rotary body  50 ,  50 ′ is provided, are embodied on the sides facing one another of the raised areas  55   a  and  55   b.  The raised areas  55   a  and  55   b  are embodied as axially symmetrical pairs and are disposed on the end face of the respective rotary body  50 ,  50 ′. The guideways  54   a  and  54   b  are embodied directly on the raised areas  55   a  and  55   b  of the rotary bodies  50 ,  50 ′, for instance in the form of milled recesses disposed between the raised areas  55   a  and  55   b.  They can also be embodied as flat strips, which can be secured to the opposed sides of the raised areas  55   a,    55   b.    
         [0083]    The guideways  34   a,    34   b  with which each gear wheel  30  is provided are embodied on the sides facing one another of the raised areas  35   b.  They are formed by pairs facing one another in the center, which are embodied on the end face of the gear wheel  30 . The axial openings  32  of the gear wheel  30  are disposed on an arc and are distributed uniformly between the raised areas  35   a,    35   b.  The guideways  34   a,    34   b  are embodied directly on the raised areas  35   a,    35   b  of the gear wheel  30 . However, they can also be embodied as flat strips, which are fixedly embodied on the sides facing one another of the raised areas  35   a,    35   b.    
         [0084]    A conversion element  70  includes a ring, or essentially comprises a ring, both end faces of which each have two guide means  74 - 1 ,  74 - 2 ;  74 - 3 ,  74 - 4  with center axes  77 -X,  77 -Y. The center axes  77 -X of the guide means  74 - 1 ,  74 - 2  extend perpendicular to an axial plane  40   ab,  while the center axes  77 -Y of the guide means  74 - 3 ,  74 - 4  on the other end face extend parallel to the axial plane  40   ab.  In other words, the center axes  77 -X of the guide means  74 - 1 ,  74 - 2  of one end face extend perpendicular to the center axes  77 -Y of the guide means  74 - 3 ,  74 - 4  of the other end face. At the same time, the center axes  77 -X,  77 -Y of all the guide means  74 - 1 ,  74 - 2 ,  74 - 3 ,  74 - 4  extend perpendicular to the rotary axis  40   a,  and more precisely perpendicular to planes in which the rotary axis  40   a  is located or which are formed by the rotary axis  40   a.  That is, an annular plane formed by the ring and located parallel to the end faces extends perpendicular to the rotary axis  40   a,  and the center axes  77 -X,  77 -Y of the guide means  74 - 1 ,  74 - 2 ,  74 - 3 ,  74 - 4  extend parallel to this annular plane. The center axes  77 -X and  77 -Y of the guide means  74 - 1 ,  74 - 2  and  74 - 3 ,  74 - 4 , respectively, on a given side coincide and are oriented radially, but they could also be disposed spaced apart from one another, in which case they would not be oriented radially. The ring or conversion element  70  furthermore has continuous, axially oriented openings  78 , which the spacers  52  of the rotary body  50  pass through without contact. By means of the spacers  52 , the two rotary bodies  50 ,  50 ′ forming the output member are connected non-rotatably to one another. 
         [0085]    The guide means  74 - 1 ,  74 - 2 ,  74 - 3 ,  74 - 4  have guideways  74   a,    74   b;    75   a,    75   b,  which in a cross section viewed perpendicular to the rotary axis are preferably trapezoidal. However, they could also be embodied as convex or concave. 
         [0086]    Cylindrical roller elements  80  are disposed between the guideways  54   a  and  54   b  of the linear guide  50   b  of the rotary body  40  and the guideways  75   a,    75   b  of the conversion element  70 , by which guideways the conversion element  70  is disposed displaceably in the linear guide  50   b.  Cylindrical roller elements  90  are also disposed between the guideways  34   a  and  34   b  of the linear guide  30   b  on the gear wheel  30  and the guideways  74   a,    74   b  of the conversion element  70 , by which guideways the conversion element  70  is disposed displaceably in the linear guide  30   b.  In both cases, guidance of the conversion element  70  by means of roller elements  80 ,  90  is ensured if the conversion element exerts its oscillatory motions, which convert the planetary motions of the gear wheels  30  into rotary motions of the output member, relative to the gear wheel  30  and relative to the rotary body  50  and the rotary axis  40   a.  To limit the guideways  74   a,    74   b,    75   a,    75   b,  boundary faces which limit the motion of the roller elements  80 ,  90  can be embodied on the guide means  74 - 1 ,  74 - 2 ,  74 - 3 ,  74 - 4  of the conversion element  70 . 
         [0087]    The internal toothing  41  of the main body  40  comprises needle-like roller bodies  41   b,  which are supported in axial slots  41   a  on the inner circumference of the main body  40 . The axial slots  41   a  are distributed uniformly on the inner circumference of the main body  40 . Accordingly, they are gear wheels whose teeth comprise preferably horizontal cylinders. The external toothing  33  of the gear wheel  30  is correspondingly embodied in undulating form. 
         [0088]    The spacers  52  are disposed on the raised areas  55   a  and  55   b  of the rotary body  50 . These spacers  52  pass through the axial openings  30  of the gear wheel  30  with play and are provided with axial recesses  53  and threaded recesses  59 . The axial recesses  53  and the threaded recesses  59  are provided for receiving the connecting elements  60 . The connecting elements  60  may be embodied as pins or as screws  60 , for example. As a result of tightening of the connecting elements  60  embodied as screws  60 , the end faces of the spacers  52  define the position of the two rotary bodies  50 ,  50 ′. 
         [0089]    In contrast to the rotary body  50 , the rotary body  50 ′ has no spacers  52 . Instead, the rotary body  50 ′ has axial recesses  53 ′ for the spacers  52 . 
         [0090]    The roller bearing between the main body  40  and the output member formed by the rotary bodies  50 ,  50 ′ can be formed by cylindrical roller elements, which roll on running surfaces  42   a  embodied on the main body  40  and the rotary body  50  and extending in a closed path around the rotary axis  40   a  ( FIG. 1 ). Alternatively, a bearing  43  can also be disposed between the main body  40  and each of the rotary bodies  50 ,  51 ′ ( FIG. 2 ). 
         [0091]    To reduce weight, the input member  10  has a continuous opening  4  extending coaxially to the rotary axis  40   a.  This opening  4  can at the same time serve to receive, and/or connect with, a drive shaft of a drive motor. 
         [0092]    Between the rotary body  50  and a retaining body not shown in detail, a seal extending all the way around may be provided, which prevents contaminants from penetrating the transmission on the driven end. 
         [0093]    It is important to emphasize that in the transmission of the invention, the input member, the output member or the main body can arbitrarily be, in principle, the driving end, the driven end, or a fixed element, without impairing the fundamental function of the transmission. Only the gear ratio is changed as a result. In the transmissions in the exemplary embodiments shown, in each case, the input member  10  is provided for being driven by a drive motor. The driven end is then formed, for instance, by the side of the main body  40  on which the rotary body  50  is supported. 
         [0094]    The invention can be employed commercially, particularly in the field of manufacturing planetary or cycloid gears, for instance, for used in industrial robots, for electric parking brakes in motor vehicles, or quite generally, for applications which demand a lightweight transmission in as compact a space as possible, and with a high gear ratio and powerful performance data.