Patent Abstract:
A spare part set for a gearmotor series includes transmissions actuated by electric motors. The series has at least one dimension which may be characterized by at least one physical, mechanical and/or geometrical value, e.g., by nominal power, axis height or torque. Each electric motor includes at least one crankcase, a rotor provided with a rotor axis and a side-shield for a motor bearing arranged within a given size. The crankcase includes an interface with the side-shield for a motor bearing, which is selected such that at least two different embodiments thereof are connectable to the said crankcase.

Full Description:
FIELD OF THE INVENTION 
     The present invention relates to an assembly set for a series of geared motors. 
     BACKGROUND INFORMATION 
     An inverter motor is described, for example, in German Published Patent Application No. 197 04 226, an inverter for supplying the motor with power being connected at the terminal box of the motor. 
     Geared motors include motors that are connected directly or indirectly to at least one gear unit. 
     German Published Patent Application No. 101 16 595 describes a series of geared motors, in which a motor shaft is connectable to a shank pinion or a plug-on pinion. However, an adapter is necessary for the plug-on pinion. 
     SUMMARY 
     An example embodiment of the present invention provides a modular system of geared motors. 
     According to an example embodiment of the present invention, an assembly set may provide that the drive-end motor bearing shield has an interface on the output side, such that
         (i) a lateral-force-free gear unit or   (ii) a gear unit not free of lateral force is directly connectable,
 
the rotor shaft being connected non-positively, integrally and/or positively on the output side to a pinion,
 
the direct connection being implemented such that the pinion is provided as the input gearing part of the gear unit.
       

     In this context, it may be provided that an interface is produced of the kind that direct mounting of a planetary gear unit or a gear unit having an input spur-gear stage is possible. The pinion may be implemented as a shank pinion and/or plug-on pinion, thereby making it possible to increase the range of gear ratios able to be covered by the assembly set considerably. 
     The pinion and rotor shaft may be in one piece, and therefore, no pinion may be necessary. In this manner, it may be possible to reduce the manufacturing tolerances. 
     The assembly set for a series of geared motors may include gear units driven by electric motors, 
     the series including at least one size able to be characterized by at least one physical, mechanical and/or geometrical variable, e.g., such as rated power output, shaft height or torque, 
     the electric motors each including at least a motor housing, a rotor including rotor shaft, and a drive-end motor bearing shield, 
     within one size, the motor housing having an interface to the motor bearing shield on the output side, such that at least two different variants of the output-side motor bearing shield are connectable to the motor housing, 
     the output-side bearing shield including a bearing for the rotor shaft, 
     (i) in a first variant, the drive-end motor bearing shield having an interface on the output side, such that the drive-end motor bearing shield is connectable to a flange of an adapter, 
     the adapter including a first adapter part and the adapter flange, 
     the assembly set including at least two types of the first adapter part connectable to the adapter flange, the interface between the adapter flange and the drive-end motor bearing shield of the first variant including a centering device, 
     the first adapter part of the first type 
     
         
         
           
             being connectable to a gear unit not free of lateral force, such as a gear unit with a helical-gear stage disposed on the input side, with the aid of an interface encompassing a two-dimensional, open fitting, thus, with the aid of an interface allowing shifts in a plane for setting the backlash of the gear unit not free of lateral force, 
             including an adapter shaft, 
             including at least two bearings and 
             having a first device for the compensation of axial expansions, e.g., thermally caused expansions,
 
the first adapter part of the second type
 
             being connectable by an interface to a lateral-force-free gear unit, such as a planetary gear unit, 
             including an adapter shaft, 
             having a second device for the compensation of axial expansions, e.g., thermally caused expansions, and 
             including one bearing,
 
(ii) in a second variant, the drive-end motor bearing shield having an interface on the output side, such that a lateral-force-free gear unit, and alternatively, a gear unit not free of lateral force, is directly connectable,
 
in the second variant, it being possible to provide at least two types of rotor shafts when working with the same housing of the motor,
 
             in the case of the rotor shaft of the first type, a plug-on pinion being provided on the output side and 
             in the case of the rotor shaft of the second type, a shank pinion being provided on the output side,
 
the direct connection being implemented such that the shank pinion or plug-on pinion is provided to mesh with at least one gearing part of the gear unit.
 
           
         
       
    
     In this context, it may be provided that servo gear units, such as planetary gear units and other low-backlash gear units, are connectable to a motor either directly or via an adapter. Therefore, the unit volume, torsional rigidity and mass moment of inertia of the geared motor are also adaptable to the requirements of the specific application, without many parts being necessary, for in spite of the few parts included, the modular system may provide an extremely large variance within each size. 
     In an example embodiment, all the gear units have an open fitting as interface on the input side. This may provide that the pinion of the adapter shaft or rotor shaft to be introduced is radially displaceable together with the associated components, such that it is able to be brought to the desired position. In the case of the helical-gear stage, this means a possibility for adjusting the backlash, in the case of the planetary-gear stage, a centering of the sun wheel. 
     A bellows coupling may be provided as a first device for the compensation of axial expansions. Provided as a second device for the compensation of axial expansions may be at least one compensating disk, e.g., at a bearing of the adapter part. This may provide that it is possible to compensate for location and position deviations of the shafts, thus, the adapter shaft and the rotor shaft, and also for thermally caused expansions in a simple, cost-effective manner. 
     The gear units of the series may be designed to be low-backlash, such that, e.g., after adjusting the backlash with the aid of the displacements, the backlash on the whole may be less than 3 angular minutes per individual gear stage and/or gear unit. An advantage is that the gear units may be usable for servo technology. 
     The lateral-force-free gear unit connected to the adapter part and having a bearing arrangement on one side may encompass a higher air volume for the pressure equalization than the lateral-force-free gear unit having a bearing arrangement on both sides. Thermally caused air-pressure increases may be reducible, and therefore the danger of the gear unit becoming leaky may be decreased. 
     The gear unit may have a planetary-gear stage as input stage. This may provide that a servo gear unit free of lateral force on the input side and having a high gear ratio may be provided. 
     The gear unit not free of lateral force may be a double-stage gear unit whose gear stage situated on the input side is implemented as a spur-gear stage, e.g., having helical-toothed gear wheels. A high gear ratio may thus be attainable in the case of this double-stage gear unit, and the input spur-gear stage may be produced inexpensively. 
     The second stage of the gear unit not free of lateral force may be a right-angle gear stage. Not only colinear servo gear units, but also right-angle servo gear units may be produced using a small number of parts. 
     The right-angle gear unit may be arranged to be single-stage, e.g., as a hypoid gear unit. In this manner, a non-colinear gear unit having a high gear ratio may be produced within the series. 
     The gear units may be servo gear units, e.g., for exact positioning. 
     Further features and aspects hereof are described below. 
     LIST OF REFERENCE NUMERALS 
     
         
           1  motor housing 
           2  rotor with cylindrical shaft end 
           3  rotor with feather key for plug-on pinion 
           4  rotor for shank pinion 
           5  adapter part with two bearings 
           6  adapter part with one bearing 
           7  right-angle gear unit 
           8  planetary gear unit with cylindrical output-shaft end 
           9  planetary gear unit with flange block output 
           10  planetary gear preliminary stage 
           11  adapter flange 
           12  motor bearing shield with bearing 
           13  motor bearing shield with bearing 
           14  motor bearing shield with bearing 
           21  centering bore 
           22  rotor shaft 
           23  motor bearing shield 
           24  interface 
           25  bearing 
           26  shaft seal ring 
           31  plug-on pinion 
           32  rotor shaft 
           33  motor bearing shield 
           35  bearing 
           36  shaft seal ring 
           41  shank pinion 
           42  rotor shaft 
           45  bearing 
           46  shaft seal ring 
           50  gear-side coupling half 
           51  centering bore 
           52  adapter shaft 
           53  plug-on pinion 
           54  shaft seal ring 
           55  bearing 
           56  housing of the adapter part 
           57  bearing 
           58  motor-side coupling half 
           59  metal bellows 
           60  fastening screw 
           61  clamping ring 
           62  adapter flange 
           63  slit 
           64  housing of the adapter part 
           65  bearing 
           66  shaft seal ring 
           67  adapter shaft 
           68  centering bore 
           69  shank pinion 
           70  spur gear 
           71  bearing 
           72  pinion 
           73  crown-toothed wheel 
           74  open fitting 
           75  housing part 
           76  shaft 
           80  centering bore 
           81  planet-carrier shaft 
           82  shaft seal ring 
           83  bearing 
           84  bearing 
           85  needle bearing 
           86  planet wheel 
           87  planet spindle 
           88  spatial volume 
           89  clamping nut 
           90  bearing 
           91  planet spindle 
           92  planet wheel 
           93  housing 
           94  shaft seal ring 
           95  planet carrier 
           96  screw plug 
           97  spatial volume 
           98  needle bearing 
           121  asynchronous motor 
           122  synchronous motor with square flange 
           123  asynchronous motor as servo motor 
           124  inverter motor 
           125  series-connected gear unit 
           126  adapter 
           127  helical gear unit 
           128  parallel-shaft gear unit 
           129  helical-bevel gear unit 
           130  worm gear unit 
           131  spiroplan gear unit 
       
    
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         FIG. 1  illustrates a series part, the components being illustrated in combination possibilities. 
         FIG. 10  illustrates a further part of the series, the components being illustrated in combination possibilities. 
         FIGS. 2 to 4  illustrate motor bearing shields  12  to  14  of the motors as individual parts. 
         FIGS. 5 and 6  illustrate individual adapter parts  5 ,  6  and  11 . 
         FIGS. 8 and 9  illustrate planetary-gear-unit parts. 
         FIG. 7  illustrates right-angle gear unit  7  illustrated in  FIG. 1  as an individual part. 
         FIG. 11  illustrates a double-stage right-angle gear unit with an adapter. 
         FIG. 12  illustrates a planetary gear unit with an adapter. 
         FIG. 13  illustrates a planetary gear unit with an adapter. 
     
    
    
     DETAILED DESCRIPTION 
       FIG. 10  illustrates combination possibility for a series of gear units. In this context, the assembly set for the series of geared motors is arranged such that different motors are connectable to different gear units, directly or with the aid of an adapter. The gear units illustrated in  FIG. 10  do not have to be implemented as servo gear units. 
       FIG. 1  illustrates a part that is compatible with the series of geared motors, thus has corresponding interfaces. This part includes servo geared motors that are able to be assembled in various combinations. The gear units illustrated in this context and connectable to the motors are servo gear units. 
     This part illustrated in  FIG. 1  is discussed first of all in the following: 
     The motor includes a motor housing  1  with stator. Depending on the requirement, an encoder and/or a brake is/are connectable on the non-drive end. On the drive end, the housing has an interface for connection to a motor bearing shield  12 ,  13 ,  14 . The interface is formed by the drive-end geometrical formation of the motor housing and the positioning of the bores. The matching counter-interface is implemented in motor bearing shield  12 ,  13 ,  14 . Thus, motor housing  1  is connectable to all motor bearing shields  12 ,  13 ,  14 , each of which in turn differs at other points, however. The associated seats of the bearings and/or shaft-seal-ring seats may be implemented differently and/or different rotor shafts may be accommodated. Rotor  2 ,  3 ,  4 , including in each case the rotor shaft, may be selected differently. A non-drive-end bearing of rotor  2 ,  3 ,  4  is encompassed by the motor housing. The further drive-end bearing is encompassed by the motor bearing shield. 
     Rotor  2  is implemented with a drive-end, cylindrical shaft end. This is also illustrated clearly in  FIG. 2 . In this context, rotor shaft  22  of rotor  2  also includes a centering bore  21 . Motor bearing shield  23  includes a bearing seat for bearing  25  and a shaft-seal-ring seat for shaft seal ring  26 . Interface  24  is implemented in the manner mentioned above in the case of the motor bearing shield and the motor housing. 
     As illustrated in  FIG. 3 , rotor  3  is implemented with rotor shaft  32 , rotor shaft  32  being supported by bearing  35  in motor bearing shield  33 , which corresponds to motor bearing shield  12 , and being sealed against it by shaft seal ring  36 . Interface  24  of motor bearing shield  33  is implemented to match the same motor housing, as also in the case of  FIG. 2 . Rotor shaft  32  of rotor  3  is connected on the drive end by a feather key to a plug-on pinion  31 . 
     As illustrated in  FIG. 4 , rotor  4  is implemented with rotor shaft  42 , rotor shaft  42  being supported by bearing  45  in motor bearing shield  33 , which corresponds to motor bearing shield  12 , and being sealed against it by shaft seal ring  46 . Interface  24  of motor bearing shield  33  is implemented to match the same motor housing, as also in the case of  FIG. 2 . Rotor shaft  42  of rotor  4  is connected on the drive end to a shank pinion  41 . 
     In further exemplary embodiments of the present invention, rotors  2 ,  3 ,  4  are practicable in different electromechanical variants, e.g., as rotor with short-circuit cage for forming an asynchronous motor, or as rotor with pasted-on magnets for forming a synchronous motor. However, further variants of motors, such as reluctance motors, direct-current motors or other electric motors, etc., are also usable. To that end, the interface and the rotor may be implemented to match accordingly. 
     Instead of motor bearing shield  12 , motor bearing shield  14  is also usable with rotors  3  or  4 , motor bearing shield  14  having the same interface  24  toward motor housing  1 . The connection of all gear units  127 ,  128 ,  129 ,  130 , which have a corresponding flange and are illustrated in  FIG. 10 , is permitted with the aid of this motor bearing shield  14 . Gear units which, like right-angle gear unit  131 , are arranged with a motor bearing shield integrated into the gear-unit housing, are not connectable. Only upon omission of indicated motor bearing shield  14 , is it connectable. 
     In further exemplary embodiments of the present invention, each motor bearing shield may also be implemented as a square flange. Thus, further combination possibilities may be provided, with only a little more expenditure on components. 
     In the exemplary embodiment illustrated in  FIG. 1 , the motor formed with motor bearing shield  12  is connectable to a planetary gear unit with or without planetary-gear preliminary stage  10 , or to a right-angle gear unit  7 . In this context, the planetary gear unit is implemented as planetary gear unit  8  having a cylindrical output-shaft end, or as planetary gear unit  9  having a flange block output. 
     In the exemplary embodiment illustrated in  FIG. 1 , the motor formed with motor bearing shield  13  is connectable via the adapter, formed of adapter flange  11  and adapter part  6 , to a planetary gear unit with or without planetary gear preliminary stage  10 , or via the adapter formed of adapter flange  11  and adapter part  5 , to right-angle gear unit  7 . In this context, the planetary gear unit is implemented as planetary gear unit  8  having a cylindrical output-shaft end, or as planetary gear unit  9  having a flange block output. 
     Asynchronous motor  121  may be implemented as a standard motor in accordance with the IEC standard. However, further manufacturer-specific designs are also usable. One manufacturer-specific example embodiment is also illustrated in  FIG. 1 . Motor housing  1  is usable for various motors which differ due to motor bearing shield  12 ,  13 ,  14  and rotors  2 ,  3 ,  4 . For example, a rotor  4  with shank pinion and a rotor  3  with plug-on pinion may also be provided. An extremely compact, direct mounting of one of gear units  7 ,  8 ,  9 ,  10  may thereby be feasible, and it may thus be possible to dispense with adapters etc. Since shank pinions and plug-on pinions are provided within the series modular system, a wide range of gear ratios is already attainable in the spur-gear stage disposed on the input side, the indicated pinion being the input gearing part of this spur-gear stage. 
     Synchronous motor  122  is arranged with a square flange, and is therefore connectable to corresponding components which have a matching interface. For example, adapter  126  or series-connected gear unit  125  are practicable on the motor side with such an interface. In the case of direct connection to the gear unit, gear unit  127 ,  128 ,  129  or  130  is also feasible with such a flange. As illustrated in  FIG. 10 , however, gear units  127 ,  128 ,  129  and  130 , adapter  126  and series-connected gear unit  125  are implemented with a round flange. Not only asynchronous motor  121 , but also asynchronous motor  123 , implemented as a servo motor, or inverter motor  124  are connectable to the indicated round flanges 
     Series-connected gear unit  125  includes a double-stage or triple-stage helical gear unit, and may be used for applications having a very high gear reduction. 
     Adapter  126  is connectable on the output side to gear unit  127 ,  128 ,  129  or  130 . Therefore, the oil chamber of gear unit  127 ,  128 ,  129  or  130  may remain closed upon exchange of motor  121 ,  122 ,  123 ,  124  arranged at adapter  126  at the drive end. 
     Series-connected gear unit  125  and adapter  126  may also be provided with a square flange on the input side. 
     Parallel-shaft gear unit  128  and helical gear unit  127  each include two or three spur-gear stages. Helical-bevel gear unit  129  includes a spur-gear stage arranged on the input side and a bevel-gear stage disposed on the output side. Worm gear unit  130  includes a spur-gear stage arranged on the input side and a worm-gear stage disposed on the output side. Spiroplan gear unit  131  includes a spiroplan gear stage, thus, a right-angle gear stage. 
     A gear unit free of lateral force on the input side, e.g., planetary gear unit  8 ,  9 ,  10 , may be connectable to a motor in the same manner as a gear unit not free of lateral force on the input side, e.g., a gear unit having a spur-gear stage disposed on the input side, like gear unit  7 . The gear-side interface of the motor, or of the motor plus adapter, is thus identical for lateral-force-free gear units and gear units not free of lateral force. 
     The mass moment of inertia may be selectable, and therefore adaptable to the customer application, thus, the driven load. Thus, if a high mass moment of inertia is desired, and even a low torsional rigidity, a geared motor with adapter is selected, e.g., components  1 ,  2 ,  13 ,  11 ,  6 ,  8  or components  1 ,  2 ,  13 ,  11 ,  5 ,  7  illustrated in  FIG. 1 . A low torsional rigidity also means an, e.g., “smoother” drive; thus, sudden changes in torque of the geared motor are absorbed to a certain extent. If, on the other hand, a low mass moment of inertia and a high torsional rigidity are needed, a geared motor without adapter, thus, with motor connected directly to the gear unit, is selected, e.g., components  1 ,  3 ,  12 ,  7  or components  1 ,  3 ,  12 ,  8  or components  1 ,  4 ,  12 ,  9  illustrated in  FIG. 1 . 
     The gear units, e.g., gear units  7 ,  8 ,  9 ,  10 , are designed with low backlash, e.g., with a backlash of less than 3 angular minutes per gear stage. 
     The motor-side interface of adapter flange  11  may be implemented with very little tolerance, thus highly precisely. Thus, the motor with its motor bearing shield  13  may be able to be disassembled very precisely. For example, the indicated interface may be implemented with less tolerance, thus, more precisely than the interface of the adapter toward the gear unit. 
       FIG. 5  is a sectional view of the adapter including adapter part  5  and adapter flange  11 .  FIG. 6  is a sectional view of the adapter including adapter part  6  and adapter flange  11 . In common—and therefore reusable within the modular system—is adapter flange  62 , which is connected to the housing of adapter part  5  or  6  by fastening screws  60 . 
     As illustrated in  FIG. 5 , the cylindrical shaft end of rotor shaft  2  is connectable with the aid of clamping ring  61  to motor-side coupling half  58 , which has a slit that may make the clamping effect of clamping ring  61  predictable and definable. Gear-side adapter shaft  52  of the adapter has a centering bore  51  and is connected to a plug-on pinion  53 . Adapter shaft  52  is sealed by shaft seal ring  54  against housing  56  of adapter part  5 , and is supported in it by bearings  55 ,  57 , bearing  57  being sealingly implemented, and therefore a certain sealing of the lubricant, e.g., grease or semi-fluid grease, toward the motor being achieved. Toward the gear unit, e.g., toward its interior chamber having a different lubricant such as oil, etc., the sealing may be achieved by shaft seal ring  54 . Between shaft seal ring  54  and bearing  55 , an annular space is partially filled with lubricant, e.g., grease or semi-fluid grease, and thus a storage volume for lubricant may be provided. 
     Gear-side coupling half  50  is connected, e.g., positively, non-positively and/or integrally, to adapter shaft  52 . The metal bellows is welded at its respective axial end areas to gear-side coupling half  50  and motor-side coupling half  58 . It thus transmits the entire torque. The use of the adapter encompassing this metal bellows  59  thus may make available a geared motor having low torsional rigidity. Because of the large mass of the rotating parts, e.g., of the adapter, as well, this geared motor then also may exhibit a high moment of inertia or mass moment of inertia. The interface of the adapter toward the gear unit is implemented as a so-called open fitting, and therefore may allow small relative, radial displacements. Consequently, upon insertion of plug-on pinion  53  into gear unit  7 , plug-on pinion  53  itself and adapter shaft  52 , as well as housing  56  of adapter part  5  are fixed in that position and alignment predefined essentially by the position of the gearing parts of gear unit  7 . Therefore, the gear unit is already adjustable during manufacturing, and the connection of the adapter may not disturb the adjustments of the gear unit. Compensation is thus made for small deviations caused by manufacturing, by shifting or rotating adapter shaft  52  in the space. The setting of the distance between axes, and thus also the backlash of the input spur-gear stage of gear unit  7  may be adjustable by radial shift of housing  56  toward the housing of gear unit  7 . The indicated shifts are on the order of magnitude of one or several tenths. In this connection, the backlash is adjustable such that it may be less than 3 angular minutes. 
     On the other hand, adapter flange  62  has an interface toward the motor, such that the motor together with rotor shaft  2  may be exactly positioned upon being screwed onto adapter flange  62 , i.e., the spatial position and alignment of motor bearing shield  13  with motor housing  1  and rotor shaft  2  is established by the screwing-on process. To that end, adapter flange  62  is provided at its interface with a fitting, and motor bearing shield  13  is provided with a corresponding formation. Metal bellows  59  accommodates radial and axial deviations from an ideal position. 
     The motor has components made of different materials. For example, the stator, e.g., also motor housing  1 , is of aluminum, the rotor, e.g., the rotor shaft, of steel. Therefore, different thermal expansions may result, which also take effect in the direction of the adapter. To compensate for these expansions, motor-side coupling half  58  and gear-side coupling half  50  have an axial distance relative to each other of, for example, one or several millimeters. In response to thermally caused linear expansions of the rotor shaft, compensation is thus made possible by metal bellows  59 . 
     As illustrated in  FIG. 6 , the cylindrical shaft end of rotor shaft  2  is connectable with the aid of clamping ring  61  to adapter shaft  67 , which has a slit  63  that may make the clamping effect of clamping ring  61  predictable and definable. In addition, in the area of motor-side slit  63 , adapter shaft  67  is implemented as a hollow shaft for the insertion of the rotor shaft. Adapter shaft  67  of the adapter is connected to a shank pinion  69  that has a centering bore  68 . Adapter shaft  67  is sealed by shaft seal ring  66  against housing  64  of adapter part  6  and is supported in it by bearing  65 . Bearing  65  is sealingly implemented toward the motor. Between shaft seal ring  66  and bearing  65 , an annular space is partially filled with lubricant, e.g., grease or semi-fluid grease, and thus a storage volume for lubricant is provided. 
     Thus, the adapter illustrated in  FIG. 6  may make available a geared motor having high torsional rigidity. Because of the smaller mass of the rotating parts, e.g., also of the adapter, in comparison to the adapter illustrated in  FIG. 5 , this geared motor may exhibit a low moment of inertia or mass moment of inertia. The interface of the adapter toward the gear unit is implemented as a so-called open fitting, and therefore may allow small relative, radial displacements. Therefore, upon insertion of plug-on pinion  69  into gear unit  8 ,  9  or  10 , shank pinion  69  itself and adapter shaft  67 , as well as housing  64  of adapter part  6  are fixed in the position and alignment essentially predefined by the position of the gearing parts of gear unit  8 ,  9  or  10 , e.g., by the planets of the input planetary-gear stage of gear unit  8 ,  9  or  10 . Consequently, the gear unit is already adjustable during manufacturing, and the connection of the adapter may not disturb the adjustments of the gear unit. Compensation is thus made for small deviations caused by manufacturing, by shifting or rotating adapter shaft  67  in the space. Because, for example, of the use of plug-on pinion  69  as sun wheel of the input stage of gear unit  8 ,  9  or  10 , the spatial volume for movement of shank pinion  69  upon insertion into gear unit  8 ,  9  or  10  may be sharply limited. However, the open fitting may permit the exact final position of the housing of adapter part  6  and of the housing of gear unit  8 ,  9  or  10  relative to each other to adapt to the position of the sun wheel predefined by that of the planets. 
     On the other hand, adapter flange  62  has an interface toward the motor, such that the motor together with rotor shaft  2  may be exactly positioned upon being screwed onto adapter flange  62 , i.e., the spatial position and alignment of motor bearing shield  13  with motor housing  1  and rotor shaft  2  is established by the screwing-on process. To that end, adapter flange  62  is provided at its interface with a fitting, and motor bearing shield  13  is provided with a corresponding formation. 
     To compensate for thermal expansions, compensating disks are inserted as elastic rings in the region of bearing  65 . Therefore, thermal expansions may be essentially passed on to shank pinion  69  and are compensated in gear unit  8 ,  9  or  10 , since the sun wheel and planets may be shiftable relative to each other by small amounts without considerable functional losses. To that end, gear unit  8 ,  9  or  10  makes spatial volume available that is provided axially in front of the upper and behind the lower end face of the sun wheel, as illustrated in  FIGS. 12 and 13 , as well. 
     A difference between the adapters illustrated in  FIGS. 5 and 6  is that the adapter illustrated in  FIG. 5  has two bearings  54 ,  57  for adapter shaft  52 , whereas only one bearing  65  is provided for adapter shaft  67 . Bearing  65  is provided as a fixation aid during assembly. Since shank pinion  69  is used as sun wheel, no take-up of lateral force may be necessary. However, the adapter illustrated in  FIG. 5  is provided for assembly with the input spur-gear stage of gear unit  7 , lateral forces then acting on plug-on pinion  53 , which are absorbed by bearings  55 ,  57 . 
       FIG. 7  illustrates gear unit  7 , thus, the right-angle gear unit, which, toward the motor, has the same interface with open fitting as the planetary gear unit. Therefore, the motor with its motor bearing shield  12  is thus connectable both to right-angle gear unit  7  and to one of planetary gear units  8 ,  9 ,  10 .  FIG. 7  illustrates the interface with open fitting  74  more precisely. The pinion connected to the adapter shaft is inserted into right-angle gear unit  7  until it engages with spur gear  70 , and the housing of the adapter part or of motor bearing shield  12  abuts axially against the housing of gear unit  7 . Additionally, a relative radial shift of the housing is then carried out such that the desired amount of the backlash of the spur-gear stage of less than 3 angular minutes may be achieved. Finally, the connection is then secured with fastening screws in a manner resistant to fatigue. 
     Not only the adapter with adapter part  5 , but also a direct mounting of the motor with the aid of motor bearing shield  12  may be made possible, the shank pinion or plug-on pinion then being provided directly at the rotor shaft of rotor  3  or  4 . Therefore, an extremely compact type of construction may be achieved, which at the same time may be compatible with the standard motor, including rotor shaft  2  with cylindrical shaft end, via the adapter. After the connection of the adapter or motor, spur gear  70  engages with the respective pinion, a backlash of, e.g., less than three angular minutes being provided. Spur gear  70  is connected by feather keys to shaft  76 , which also encompasses pinion  72 . Shaft  76  and pinion  72  may be designed in one piece. Shaft  76  is supported by bearing  71 , which is connected to housing part  75  of gear unit  7 . Pinion  72  engages with crown-toothed wheel  73 , that is supported by a bearing in housing part  75  of gear unit  7 . 
     In  FIG. 8 , planetary gear unit  8  is illustrated enlarged as an individual part. The interface toward the motor or adapter is implemented as an open fitting in the manner already mentioned. After the connection, the pinion, thus shank pinion or plug-on pinion, connected to the rotor shaft or adapter shaft acts as the sun wheel of the planetary gear unit. Spatial volume  88  is able to compensate for thermal expansions. The spatial volume may have an axial extension toward the sun wheel, e.g., between 0.2 mm and 2 mm. The sun wheel engages with planet wheels  86  and, upon connection, is essentially codetermined in its position and alignment. Planet wheels  86  are in each case supported via one or even two needle bearings  85 , arranged axially behind each other, on planet spindles  87 , which are provided in bores of planet-carrier shaft  81 , that has a centering bore  80 . Planet-carrier shaft  81  is supported by bearings  83 ,  84  in the housing, and sealed against it by shaft seal ring  82 . Clamping nut  89  serves at its outer periphery as a bearing surface for the sealing lip of the shaft seal ring. The housing also features a recess having a screw plug for filling or emptying the lubricant. 
     Planetary gear unit  9  is illustrated enlarged as an individual part in  FIG. 9 , this planetary gear unit having a flange block interface on the output side. This interface may be implemented as an industrial robot interface in accordance with the standard EN ISO 9409-1. The interface toward the motor or adapter is implemented as an open fitting in the manner already mentioned. After the connection, the pinion, thus shank pinion or plug-on pinion, connected to the rotor shaft or adapter shaft acts as the sun wheel of the planetary gear unit. Spatial volume  97  is able to compensate for thermal expansions. The spatial volume may have an axial extension toward the sun wheel, e.g., between 0.2 mm and 2 mm. The sun wheel engages with planet wheels  92  and, upon connection, is essentially codetermined in its position and alignment. Planet wheels  92  are in each case supported via one or even two needle bearings  98 , arranged axially behind each other, on planet spindles  91 , which are provided in bores of planet-carrier shaft  95 , that has a central bore which is tightly closed by a screw plug  96 . The indicated bore may be implemented as a threaded bore, and screw plug  96  has a corresponding thread. As illustrated in  FIG. 9 , screw plug  96  is releasable for filling or emptying the lubricant, and is then connectable again. Planet-carrier shaft  95  is supported by bearing  90  in the housing and sealed against it by shaft seal ring  94 , planet carrier  95  being processed in one area at its outer periphery such that the area is usable as a bearing surface for the sealing lip of the shaft seal ring. 
       FIG. 11  illustrates the assembly of right-angle gear unit  7  with adapter part  5  and adapter flange  11 , interface  74  being implemented as an open fitting for adjusting the backlash between spur gear  70  and plug-on pinion  53 . 
       FIG. 12  illustrates the assembly of planetary gear unit  8  with adapter part  6  and adapter flange  11 , interface  74  being implemented as an open fitting for the compensation of tolerances. In this context, planet wheels  86  essentially codetermine the position and alignment of shank pinion  69  used as sun wheel, e.g., in the radial alignment. 
       FIG. 13  illustrates the assembly of planetary gear unit  9  with adapter part  6  and adapter flange  11 , interface  74  being implemented as an open fitting for the compensation of tolerances. In this context, planet wheels  92  essentially codetermine the position and alignment of shank pinion  69  used as sun wheel, e.g., in the radial alignment. 
     Thus, a connection of IEC standard motors with the aid of an adapter, or manufacturer-specific motors without adapter, may be provided to a gear unit, the manufacturer-specific motors being designed with a rotor shaft encompassing a shank pinion or plug-on pinion. Therefore, an extremely compact, direct connection to a gear unit may be made possible, which, however, may also be usable with standard motors connectable via adapter. 
     The adapters may compensate for the thermal linear expansion of the rotor shaft, and therefore the gear unit and the motor may be able to be thermally decoupled by the adapters. 
     Both single-stage or multi-stage gear units with or without lateral force may be produced on the input side, thus gear units with input helical gear stage or planetary gear stage may be connectable. Depending on the type of gear unit, the adapter may be implemented with lateral-force compensation, thus with adapter part  5 , or without lateral-force compensation, thus with adapter part  6 . Consequently, a large number of variation possibilities may be provided. 
     Moreover, the adapter may have the additional function of permitting centering of the pinion upon insertion into the gear unit. 
     In the case of the open fitting, it may be provided that prior to tightening the fastening screws, radial shifts are permitted between adapter and gear unit which are greater than corresponding shifts between adapter and motor. 
     Not only the entire right-angle gear unit may have a backlash of less than 3 angular minutes, but also the planetary gear unit and even the double-stage planetary gear unit, which is formed of planetary-gear preliminary stage  10  and planetary gear unit  9  or  8 . 
     The motor with rotor  2  may thus be implemented as a direct-mounting motor ( 1 ,  2 ,  13 ), and with another motor bearing shield  14 , which permits the connection with gear units  127 ,  128 ,  129 ,  130 ,  131  illustrated in  FIG. 10 , motor bearing shield  14  being connectable to adapter  126  or to series-connected gear unit  125 . As illustrated in  FIGS. 1 and 10 , an encircled  1  is used for the graphic illustration of this connection possibility. 
     The encircled  2  reference numeral represents that a direct connection of motor housing  1  together with rotors  3  or  4  to gear units  127 ,  128 ,  129 ,  130 ,  131  may also be made possible. To that end, motor housing  1  is provided with an interface which corresponds to the interface of the indicated gear units. 
     Therefore, not only standard gear units  127 ,  128 ,  129 ,  130 ,  131  are usable for the motor housing, but also servo gear units  7 ,  8 ,  9 . 
     The number of parts in the geared motors may be as small as possible, the reuse within the modular system may be as great as possible, and the application variants covered may be as diverse as possible. For example, both servo geared motors and standard geared motors are indicated as variants. 
     The series may be designed and implemented such that all servo gear units of  FIG. 1  have only integral gear ratios. 
     The same adapter is used in the variants illustrated in  FIG. 12  and  FIG. 13 . However, the planetary gear unit illustrated in  FIG. 13  is supported on both sides, the planetary gear unit illustrated in  FIG. 12  on one side, e.g., the output side. Therefore, adapter-side bearing  90  needs overall axial length. This overall length is taken into account by the design and overall axial length of adapter shaft  67  together with shank pinion  69  such that the shank pinion as sun wheel is inserted completely between planet wheels  92 . The same adapter is provided in  FIG. 12 . So that shank pinion  69  is completely inserted between planet wheels  92  in this planetary gear unit as well, housing  801  of the planetary gear unit is lengthened such that interface  74 , thus, the open fitting, sits at the corresponding axial position relative to the planet wheels, as also in  FIG. 13 . As illustrated in  FIG. 12 , an increased air volume is thereby formed between planet-carrier shaft  81  and the open fitting, which contributes to the reduction in air pressure in response to temperature elevation. This reduction in air pressure may be advantageous, e.g., during assembly or in the event of temperature elevations during operation. On the whole, therefore, because of the set goal of the greatest possible number of combinations, an increased overall length is accepted in one variant of the series. An advantage may be the reduction in air pressure in the event of a temperature elevation, viewed relatively with respect to a smaller unit volume of the gear unit. This may be achieved, for example, in the case of servo gear units, since there during a positioning task, high rotational speeds may occur which may lead to corresponding heating. Therefore, in the present series, the indicated increase in overall length is intentionally accepted, to thus attain two advantages, e.g., first, the combination diversity, and secondly, the reduction in air pressure. 
     In comparison to  FIG. 13 , the increased air volume may be seen clearly in  FIG. 12 . If, instead of the adapter, a motor having a drive-end bearing shield is directly attached, the air volume is formed in analogous fashion. 
     Instead of double-stage right-angle gear unit  7 , a single-stage hypoid gear unit may be provided. This may provide that the gear ratio is an integer, even if the efficiency is slightly less. 
     In the case of the indicated direct mounting, it may be provided that no coupling may be needed, and therefore the number of parts, and thus also the costs may be reduced. In addition, the type of construction may therefore be compact, as well. 
     As illustrated in  FIG. 5 , the deformation of the metal bellows compensates for thermal expansions; as illustrated in  FIG. 6 , the compensation is by displaceable bearing  65 . 
     Right-angle gear unit  7  may be configured such that on the whole, it has an integral gear ratio, e.g., in the range of 3 to 30. To achieve the different gear ratios, the gearing parts are interchanged within one size; in so doing, depending on the desired gear ratio, one set, including a crown-toothed wheel and a hypoid pinion, is exchanged for a second set, including a different crown-toothed wheel and a different hypoid pinion. In addition, the spur gears of the input gear stage are varied such that on the whole, an integral gear ratio may always be present. Given a constant distance between axes, thus within a specific size, the varying of the spur gears includes the helix angle and the profile offset. 
     For the hypoid stage of right-angle gear unit  7 , the first indicated set may be designed for the gear ratio i=3, the second set for the gear ratio i=7.5. 
     The gear ratios within one size, which, using as few different gearing parts as possible, may cover a range of gear ratios which may be as broad and densely filled as possible, are i=3, 4, 6, 8, 10, 15, 20, 25, 30, 35 and 40. In this context, the gear ratios of i=3 to 10 may be produced by the hypoid set, where i=3, and the remaining gear ratios with the set where i=7.5. 
     A series may include 6 sizes, thus 6 different distances between axes, for the spur-gear stage of right-angle gear unit  7 . All industrially customary sizes or output classes may be covered by this number. In addition, an optimal relationship between parts variety and piece number may be attainable at the same time. In the case of even larger sizes, e.g., in the megawatt range or more, the piece numbers may be small, such that the advantage of the multiple use of parts for different variants may become small, but the conceptual disadvantages may increase, for example, the material quantities, and thus the material costs for the housing, as well. 
     The sizes may be designed such that the maximally transmittable torque of the sizes is graduated in the manner M1*(2^(n−1)), n being the size numbered from 1 to 6 and M1 being the maximally transmittable torque of the smallest size, thus for n=1. 
     Deviations from the indicated formula M1*(2^(n−1)) may be, if they are less than 18%. This may be a particularly advantageous value. 
     The value M1=40 Nm may be especially advantageous, since the above-indicated advantageous part of the market for industrial gear units may thus be able to be covered, while retaining the cited advantages. 
     Values for M1 between 10 Nm and 100 nm may also be advantageous. 
     The series may include two types of low-backlash gear units, e.g., the indicated gear units with 3 angular minutes, and gear units of the same kind which, however, have 6 angular minutes. Therefore, more cost-effective gear units with 6 angular minutes and corresponding geared motors may also be able to be produced and offered.

Technology Classification (CPC): 8