EP1599929A2

EP1599929A2 - Spare part set for a gearmotor series

Info

Publication number: EP1599929A2
Application number: EP04713018A
Authority: EP
Inventors: Heinrich Zimmermann; Michael Christ; Roland Denefleh; Jürgen MEGERLE; Joachim Sander
Original assignee: SEW Eurodrive GmbH and Co KG
Current assignee: SEW Eurodrive GmbH and Co KG
Priority date: 2003-02-28
Filing date: 2004-02-20
Publication date: 2005-11-30
Also published as: US20060194666A1; EP3165796B1; US9157507B2; WO2004077644A3; BRPI0407916A; EP3165796A1; WO2004077644A8; AU2004214737A1; AU2004214737B2; WO2004077644A2; BRPI0407916B1

Abstract

The invention relates to a spare part set for a gearmotor series comprising transmissions actuated by electric motors. According to said invention, the series has at least one dimension which can be characterised by at least one physical, mechanic and/or geometrical value, in particular by nominal power, axis height or torque. Each electric motor comprises 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 comprises an interface with the side-shield for a motor bearing, which is selected in such a way that at least two different embodiments thereof are connectable to the said crankcase.

Description

Kit for a series of geared motors

Description:

The invention relates to a kit for a series of geared motors.

An exemplary converter motor is known from DE 197 04 226 A1, a converter for supplying the motor being connected to the terminal box of the motor.

Geared motors include motors that are connected at least directly or indirectly to a gearbox.

A series of geared motors is known from DE 101 16 595 A1, in which a motor shaft can be connected to a plug-in pinion or a plug-on pinion. However, an adapter is required for the slip-on pinion.

The invention is therefore based on the object of developing a modular system of geared motors.

According to the invention the object is achieved in the kit according to the features specified in claim 1, 3 or 4.

Essential features of the invention according to claim 4 are that the kit is designed such that the A-side motor bearing plate has an interface on the output side such that

(i) a shear-free transmission or

(ii) a non-shear-free transmission can be connected directly,

the rotor shaft being non-positively, materially and / or positively connected on the output side to a pinion,

wherein the direct connection takes place in such a way that the pinion is provided as a driving toothing part of the transmission. It is advantageous that such an interface is created that a direct attachment of a planetary gear or a gear with a driving spur gear stage is possible. In an advantageous embodiment, the pinion can be designed as a plug-in and / or slip-on pinion, as a result of which the range of gear ratios that can be covered with the kit can be increased considerably.

Essential features of the invention according to claim 3 are that the kit is even designed such that the pinion and rotor shaft are formed in one piece and thus advantageously no pinion is necessary. In addition, the manufacturing tolerances can be reduced in this way.

Essential features of the invention according to claim 4 are that the kit for a series of geared motors comprises gears driven by electric motors,

the series comprising at least one size that can be identified by at least one physical, mechanical and / or geometric size, in particular such as nominal power, axle height or torque,

wherein the electric motors each comprise at least one motor housing, a rotor, comprising a rotor shaft, and an A-side motor end shield,

wherein the motor housing of the motor has an interface to the output-side motor bearing plate in such a size that at least two different variants of the output-side motor bearing plate can be connected to the motor housing,

the bearing plate on the output side comprises a bearing for the rotor shaft,

(i) in a first variant, the A-side motor bearing plate has an interface on the output side such that the A-side motor bearing plate can be connected to an adapter flange of an adapter,

the adapter comprising a first adapter part and the adapter flange, the kit comprising at least two types of the first adapter part which can be connected to the adapter flange, the interface between the adapter flange and the A-side motor bearing plate of the first variant comprising means for centering,

the first adapter part in the first type

an adapter shaft can be connected to a non-transverse force-free transmission, such as a transmission with a spur gear stage arranged on the input side, by means of an interface comprising a two-dimensional open fitting, that is to say by means of displacements in one plane for adjusting the play of the non-transverse force-free transmission,

- comprises at least two camps and

has first means for compensating axial expansions, in particular expansions caused by heat,

wherein the first adapter part can be connected in a second way to a shear force-free transmission, such as a planetary transmission, by means of an interface, comprises an adapter shaft, has second means for compensating for axial expansions, in particular expansions caused by heat, and

- includes a warehouse,

(ii) in which, in a second variant, the A-side motor end shield has an interface on the output side such that a transmission free of lateral force and alternatively a non-lateral force transmission can be connected directly,

wherein in the second variant, at least two types of rotor shafts can be provided for the same housing of the motor, - a slip-on pinion being provided on the output side of the rotor shaft of the first type and

a plug-in pinion is provided on the output side of the rotor shaft of the second type,

wherein the direct connection takes place in such a way that the plug-in pinion or slip-on pinion is provided for engagement with at least one toothed part of the transmission. The advantage here is that servo gear units, such as planetary gear units and other low-backlash gear units, can be connected to a motor either via an adapter or directly. This means that the volume, torsional rigidity and inertia of the geared motor can also be adapted to the requirements of the respective application without the need for many parts. Because the modular system offers an extremely large variance within each size despite the few included parts.

In an advantageous embodiment, all gears have an open fitting on the input side as an interface. The advantage here is that the pinion of the adapter shaft or rotor shaft to be inserted is radially displaceable together with the associated one

Component that it can be brought into the desired position. With the spur gear stage this means an adjustment option for the game, with the planetary gear stage centering the sun gear.

In an advantageous embodiment, a bellows coupling is provided as the first means for compensating for axial expansions. Alternatively, in an advantageous embodiment, at least one shim is provided as the second means for compensating axial expansions, in particular on a bearing of the adapter part. The advantage here is that the position and positional deviations of the shafts, that is to say the adapter shaft and the rotor shaft, can be compensated for in a simple and cost-effective manner and thermal expansion can also be compensated for.

In an advantageous embodiment, the transmissions of the series are designed with little play, in particular after the play has been set by means of the displacements, that the play is less than 3 angular minutes per individual gear stage and / or transmission as a whole. The advantage here is that the gears can be used for servo technology.

In an advantageous embodiment, the shear-free gear connected to the adapter part with one-sided bearing comprises a higher air volume for pressure compensation than the shear-force-free gear with double-sided bearing. The advantage here is that thermally caused increases in air pressure can be reduced and thus the risk of the transmission leaking can be reduced. In an advantageous embodiment, the transmission has a planetary gear stage as the driving stage. The advantage here is that a servo gear with a high gear ratio is provided on the input side without lateral force.

In an advantageous embodiment, the non-shear force-free gear is a two-stage gear, the gear stage arranged on the input side is designed as a spur gear stage, in particular with helical toothed gears. The advantage here is that a high gear ratio can be achieved with this two-stage gearbox and the driving spur gear stage can be produced inexpensively.

In an advantageous embodiment, the second stage of the non-transverse force-free gear is an angular gear stage. The advantage here is that not only colinear servo gear units but also angular servo gear units can be manufactured with a small number of parts.

In an advantageous embodiment, the angular gear is designed in one stage, in particular as a hypoid gear. The advantage here is that a non-colinear gear with a high gear ratio can be produced within the series in this way.

In an advantageous embodiment, the gearboxes are servo gearboxes, in particular are therefore provided for precise positioning.

Further advantages result from the subclaims.

The invention will now be explained in more detail with reference to figures:

Figure 1 shows an essential part of the series of the invention, the components are illustrated in their possible combinations.

FIG. 10 shows a further part of the series, the components also being illustrated in their possible combinations.

Figures 2 to 4 show the motor end plates 12 to 14 of the motors as individual parts.

FIGS. 5, 6 and 11 show the individual adapter parts 5, 6 and 11.

Figures 8, 9 and 10 show the planetary gear parts.

Figure 7 shows the bevel gear 7 of Figure 1 as a single part.

Figure 11 shows a two-stage bevel gear with adapter.

Figure 12 shows a planetary gear with adapter.

Figure 13 shows a planetary gear with adapter.

FIG. 10 shows the possible combinations in a series of transmissions. The kit for the series of geared motors is designed in such a way that different motors can be connected to different gearboxes directly or using an adapter. The gearboxes shown in FIG. 10 need not be designed as servo gearboxes.

FIG. 1 shows an essential part of the invention that is compatible with the series of geared motors, that is to say has corresponding interfaces. This part, which is essential to the invention, includes servo geared motors which are available in different

Combinatorics can be put together. The gears shown and connectable to the motors are servo gears. In the following, this part, shown in FIG. 1, will now be dealt with first:

The motor comprises a motor housing 1 with a stator. Depending on requirements, an encoder and / or a brake can be connected on the B side. On the A side, the housing has an interface for connection to an engine end shield 12, 13, 14. The interface is formed by means of the A-side geometric shape of the motor housing and the positioning of the holes. The appropriate counter interface is shown in the motor end shield 12, 13, 14. Thus, the motor housing 1 can be connected to all motor end shields 12, 13, 14, which in turn differ in other places. In particular, the associated bearing seats of the bearings and / or shaft sealing ring seats can be designed differently and / or different rotor shafts can be accommodated. The rotor 2, 3, 4, each comprising the rotor shaft, is to be selected differently. A B-side bearing of the rotor 2, 3, 4 is encompassed by the motor housing. The other A-side bearing is covered by the motor end shield.

The rotor 2 is designed with an A-side cylindrical shaft end. This is also clearly shown in Figure 2. The rotor shaft 22 of the rotor 2 also includes a centering bore 21. The motor end shield 23 includes a bearing seat for the bearing 25 and a shaft seal seat for the shaft seal ring 26. The interface 24 is designed in the manner mentioned above for the motor end shield and the motor housing, the bores and screws for connecting the motor end shield and the motor housing are not shown.

The rotor 3 is designed according to FIG. 3 with the rotor shaft 32, the rotor shaft 32 being mounted by means of the bearing 35 in the motor bearing plate 33, which corresponds to the motor bearing plate 12, and being sealed against it by means of the shaft sealing ring 36. The interface 24 of the motor end shield 33 is in turn designed to match the same motor housing as in FIG. 2. The rotor shaft 32 of the rotor 3 is connected on the A side by means of a feather key to a slip-on pinion 31.

The rotor 4 is designed according to FIG. 4 with the rotor shaft 42, the rotor shaft 42 being mounted by means of the bearing 45 in the motor bearing plate 33, which corresponds to the motor bearing plate 12, and sealed against it by means of the shaft sealing ring 46. The interface 24 of the motor end shield 33 is in turn suitable for the same motor housing executed, as in Figure 2. The rotor shaft 42 of the rotor 4 is connected on the A side with a plug-in pinion 41.

In further exemplary embodiments according to the invention, the rotor 2, 3, 4 can be implemented in various electromechanical variants, in particular as a rotor with a short-circuit cage to form an asynchronous motor or as a rotor with adhesively bonded magnets to form a synchronous motor. However, other variants of motors can also be used, such as reluctance motors, direct current motors or other electric motors. The interface and the rotor must be designed accordingly.

Instead of the motor bearing plate 12, the motor bearing plate 14 with the rotors 3 or 4 can also be used, the motor bearing plate 14 having the same interface 24 to the motor housing 1. By means of this motor end shield 14 it is now possible to connect all gears 127, 128, 129, 130 which have a corresponding flange and are shown in FIG. 10. Gear units which, like the angular gear unit 131, are designed with a motor end shield integrated in the gear housing, cannot of course be connected. It can only be connected if the motor end shield 14 is omitted.

In further exemplary embodiments according to the invention, each motor end shield can also be designed as a square flange. This results in further possible combinations with only a little more component work.

In the exemplary embodiment according to FIG. 1, the motor formed with the motor end shield 12 can be connected to a planetary gear with or without planetary gear preliminary stage 10 or to an angular gear 7. The planetary gear is designed as a planetary gear 8 with a cylindrical output shaft end or as a planetary gear 9 with a flange block output.

In the exemplary embodiment according to FIG. 1, the motor formed with the motor end shield 13 is via the adapter formed from the adapter flange 11 and the adapter part 6 with a planetary gear with or without planetary gear preliminary stage 10 or via the adapter formed with the adapter flange 11 and the adapter part 5 with the angular gear 7 connectable. The planetary gear is designed as a planetary gear 8 with a cylindrical output shaft end or as a planetary gear 9 with a flange block output. The asynchronous motor 121 can be designed as a standard motor according to the IEC standard. However, other proprietary designs can also be used. An inventive embodiment of the manufacturer is also shown in FIG. 1. The motor housing 1 can be used for various motors which differ in terms of the motor end shield 12, 13, 14 and rotors 2, 3, 4. In particular, a rotor 4 with a pinion and a rotor 3 with a pinion can also be provided. As a result, an extremely compact direct attachment of one of the gears 7, 8, 9, 10 can be carried out and thus adapters and the like can be saved. Since the plug-in pinion and slip-on pinion are provided within the modular system of the series according to the invention, a wide range of gear ratios can already be achieved in the spur gear stage arranged on the input side, said sprocket being a driving toothing part of this spur gear stage.

The synchronous motor 122 is designed with a square flange and can therefore be connected to corresponding components which have a suitable interface. In particular, the adapter 126 or the primary gear 125 can be implemented on the engine side with such an interface. When directly connected to the gearbox, the gearbox 127, 128, 129 or 130 can also be designed with such a flange. In Figure 10, the gear 127, 128, 129 and 130, the adapter 126 and the primary gear 125 are designed with a round flange. Not only the asynchronous motor 121 but also the asynchronous motor 123 designed as a servomotor or the converter motor 124 can be connected to the round flanges mentioned.

The primary gear 125 comprises a two- or three-stage spur gear and is advantageously used for applications with a very high reduction ratio.

The adapter 126 can be connected to the transmission 127, 128, 129 or 130 on the output side. Thus, the oil space of the transmission 127, 128, 129 or 130 advantageously remains closed when the motor 121, 122, 123, 124 arranged on the drive side of the adapter 126 is replaced.

In further exemplary embodiments, the primary gear 125 and the adapter 126 are also provided with a square flange on the input side.

The flat gear 128 and the spur gear 127 each comprise two or three spur gear stages. The bevel gear 129 comprises a spur gear stage arranged on the input side and a bevel gear stage arranged on the output side. The Worm gear 130 comprises a spur gear stage arranged on the input side and a worm gear stage arranged on the output side. The spiroplan gear 131 comprises a spiroplan gear stage, that is to say an angular gear stage.

A major advantage of the present modular system is that a gearbox that is free of lateral force on the input side, for example the planetary gearbox 8, 9, 10, can be connected to a motor as well as a gearbox that is not free of lateral force on the input side, for example a gearbox with a spur gear stage arranged on the input side like the gearbox 7 The interface on the gearbox side of the engine or the engine plus adapter is therefore the same for non-overhung gear and non-overhung gear.

Another major advantage is that the inertia can be selected and can therefore be adapted to the customer application, that is to say the driven load. If a high mass inertia is desired and even a low torsional stiffness, a geared motor with adapter is selected, for example components 1, 2, 13, 11, 6, 8 or components 1, 2, 13, 11, 5, 7 from FIG. 1 A low torsional stiffness also means, so to speak, a "softer" drive; torque shocks are therefore absorbed to a certain extent by the geared motor. If, on the other hand, low inertia and high torsional rigidity are required, a geared motor without an adapter, i.e. with a motor directly connected to the gearbox, is selected, e.g. components 1, 3, 12, 7 or components 1, 3, 12, 8 or the components 1, 4, 12, 9 from Figure 1.

The gears, in particular the gears 7, 8, 9, 10, are designed with little play, namely with a play of less than 3 angular minutes per gear stage.

The motor-side interface of the adapter flange 11 is designed with very little tolerance, that is to say with high precision. The motor with its motor end shield 13 can therefore be removed very precisely. In particular, the interface mentioned is designed with less tolerance, that is to say more precisely, than the interface of the adapter to the transmission.

FIG. 5 shows the adapter comprising the adapter part 5 and the adapter flange 11 in a sectional view. FIG. 6 shows the adapter comprising the adapter part 6 and the adapter flange 11 in a sectional illustration. Together - and thus reusable within the modular system - is the adapter flange 62, which is connected to the housing of the adapter part 5 or 6 by means of the connecting screws 60. In FIG. 5, the cylindrical shaft end of the rotor shaft 2 can be connected by means of the clamping ring 61 to the coupling half 58 on the motor side, which has a slot for this purpose, which makes the clamping effect of the clamping ring 61 predictable and definable. The gearbox-side adapter shaft 52 of the adapter has a center hole 51 and is with a

Slip pinion 53 connected. The adapter shaft 52 is sealed by means of the shaft sealing ring 54 against the housing 56 of the adapter part 5 and is supported therein by means of the bearings 55, 57, the bearing 57 being sealed and thus a certain seal of the lubricant, in particular grease or fluid grease, towards the engine is reached. The seal by means of the shaft sealing ring 54 is achieved towards the gearbox, in particular towards its interior with a different lubricant, such as oil or the like. Between the shaft sealing ring 54 and the bearing 55, an annular space is partially filled with lubricant, in particular grease or fluid grease, and thus a supply volume for lubricant is available.

The transmission-side coupling half 50 is connected to the adapter shaft 52, in particular in a form-fitting, force-fitting and / or material-locking manner. The metal bellows is welded to the transmission-side coupling half 50 and the motor-side coupling half 58 at its axial end regions. It therefore transmits the entire torque. The use of the adapter comprising this metal bellows 59 thus provides a geared motor with low torsional rigidity. Because of the large mass of the rotating parts, in particular also of the adapter, this geared motor then also has a high moment of inertia or mass inertia. The interface of the adapter to the gearbox is designed as a so-called open fitting and therefore allows small relative, radial displacements. Thus, when inserting pinion 53 into gear 7, pinion 53 itself and adapter shaft 52 and also housing 56 of adapter part 5 are fixed in the position and orientation that is essentially predetermined by the position of the toothed parts of gear 7. That is why the gearbox can already be set during production and connecting the adapter does not interfere with the gearbox settings. Small manufacturing-related deviations are therefore caused by

Moving or rotating the adapter shaft 52 compensated in space. It is also essential that the setting of the center distance and thus also the play of the driving spur gear stage of the transmission 7 can be adjusted by means of a radial displacement of the housing 56 against the housing of the transmission 7. The displacements mentioned are in FIG on the order of one or more tenths. The game is adjustable in such a way that it is less than 3 angular minutes.

The adapter flange 62, on the other hand, has an interface to the motor in such a way that the motor together with the rotor shaft 2 is precisely positioned when it is screwed onto the adapter flange 62, that is to say that the spatial position and alignment of the motor bearing plate 13 with the motor housing 1 and the rotor shaft 2 are fixed by screwing on is laid. For this purpose, the adapter flange 62 is provided with a fitting at its interface and the motor end shield 13 with a corresponding shape. The metal bellows 59 accommodates radial and axial deviations from the ideal position

The engine has components made of different materials. For example, the stator, in particular also the motor housing 1, is made of aluminum, the rotor, in particular the rotor shaft, is made of steel. This results in different thermal expansions, which also have an effect in the direction of the adapter. To compensate for these expansions, the coupling half 58 on the motor side and the coupling half 50 on the transmission side have an axial distance of approximately one or more millimeters from one another. In the case of thermally induced linear expansion of the rotor shaft, compensation is made possible by means of the metal bellows 59.

In FIG. 6, the cylindrical shaft end of the rotor shaft 2 can be connected to the adapter shaft 67 by means of the clamping ring 61, which has a slot 63 for this purpose, which makes the clamping effect of the clamping ring 61 predictable and definable. In addition, the adapter shaft 67 is designed in the area of the slot 63 on the motor side as a hollow shaft for inserting the rotor shaft. The adapter shaft 67 of the adapter is connected to a plug-in pinion 69 which has a centering hole 68. The adapter shaft 67 is sealed against the housing 64 of the adapter part 6 by means of the shaft sealing ring 66 and is mounted in the latter by means of the bearing 65. The bearing 65 is sealed to the engine. Between the shaft sealing ring 66 and the bearing 65, an annular space is partially filled with lubricant, in particular grease or fluid grease, and thus a supply volume for lubricant is available.

The adapter according to FIG. 6 thus provides a geared motor with high torsional rigidity. Because of the lower mass of the rotating parts, in particular also of the adapter, compared to the adapter according to FIG. 5, this geared motor also has a low moment of inertia or inertia. The interface of the adapter to the gearbox is designed as a so-called open fitting and therefore leaves small relative, radial shifts too. Thus, when inserting pinion 69 into gear 8, 9 or 10, pinion 69 itself and adapter shaft 67 and also housing 64 of adapter part 6 are fixed in the position and orientation that are essentially determined by the position of the toothed parts of gear 8, 9 or 10 is specified, in particular by the planet of the driving planetary gear stage of the gear 8, 9 or 10. Therefore, the gear is already adjustable during manufacture and the connection of the adapter does not interfere with the settings of the gear. Small production-related deviations are thus compensated for by moving or rotating the adapter shaft 67 in space. In particular because of the use of the push-on pinion 69 as the sun gear of the driving stage of the gear 8, 9 or 10, the volume of space for moving the push-on pinion 69 when plugged into the gear 8, 9 or 10 is severely limited. However, the open fitting allows the exact final relative position of the housing of the adapter part 6 and of the housing of the transmission 8, 9 or 10 to be adapted to the position of the sun gear predetermined by the planet.

The adapter flange 62, on the other hand, has an interface to the motor in such a way that the motor together with the rotor shaft 2 is precisely positioned when it is screwed onto the adapter flange 62, that is to say that the spatial position and alignment of the motor bearing plate 13 with the motor housing 1 and the rotor shaft 2 are fixed by screwing on is laid. For this purpose, the adapter flange 62 is provided with a fitting at its interface and the motor end shield 13 with a corresponding shape.

To compensate for thermal expansions, shims are introduced as elastic rings in the area of the bearing 65. Thermal expansions are thus essentially passed on to the plug-in pinion 69 and compensated in the transmission 8, 9 or 10, since the sun gear and the planets can be displaced relative to one another by small amounts without significant functional losses. For this purpose, the gear 8, 9 or 10 provides space volume which is provided axially in front of the upper and behind the lower end face of the sun gear, as can also be seen in FIGS. 12 and 13.

The essential difference between the adapters according to FIGS. 5 and 6 is that the adapter according to FIG. 5 has two bearings 54, 57 for the adapter shaft 52, whereas only one bearing 65 is provided for the adapter shaft 67. The bearing 65 is essentially provided as a fixing aid during assembly. Since the insertion pinion 69 is used as a sun gear, no lateral force absorption is necessary. 5 is for assembly with the driving spur gear stage of the transmission 7 is provided, in which case transverse forces act on the slip-on pinion 53, which are absorbed by the bearings 55, 57.

FIG. 7 shows the gear 7, that is to say the angular gear, which has the same interface with open fitting to the motor as the planetary gear. Thus, the motor with its motor end shield 12 can be connected both to the angular gear 7 and to one of the planetary gear 8, 9, 10. The interface with an open fitting 74 is shown in more detail in FIG. The pinion connected to the adapter shaft is pushed into the angular gear 7 until it engages with the spur gear 70 and the housing of the adapter part or the motor end shield 12 axially strike the housing of the gear 7. Furthermore, a relative radial displacement of the housing is then carried out in such a way that the desired size of the play of the spur gear stage of less than 3 angular minutes is achieved. Finally, the connection is then permanently fixed with connecting screws.

The advantage here is that not only the adapter with adapter part 5 but also direct mounting of the motor by means of the motor end shield 12 is made possible, in which case the plug-in pinion or plug-on pinion is then provided directly on the rotor shaft of the rotor 3 or 4. A very compact design is thus achieved, which is at the same time compatible with the standard motor, comprising the rotor shaft 2 with a cylindrical shaft end, via the adapter. The spur gear 70 is in engagement with the respective pinion after the adapter or motor has been connected, with a play of less than three angular minutes being provided. The spur gear 70 is connected to the shaft 76 by means of a feather key, which also includes the pinion 72. In particular, the shaft 76 and the pinion 72 are made in one piece. The shaft 76 is held by means of the bearing 71, which is connected to the housing part 75 of the transmission 7. The pinion 72 is in engagement with the face gear 73, which is mounted in the housing part 75 of the transmission 7 by means of a bearing, not shown.

In Figure 8, the planetary gear 8 is shown enlarged as a single part. The interface to the motor or adapter is again designed as an open fitting in the manner already mentioned. The pinion connected to the rotor shaft or adapter shaft, i.e. plug-in pinion or slip-on pinion, acts as the sun gear of the planetary gear after connection. Thermal expansion can be compensated with the room volume 88. The volume of the space advantageously has an axial extension to the sun gear of between 0.2 mm and 2 mm. The sun gear is in engagement with the planet gears 86 and is at Connections are largely determined in terms of their position and orientation. The planet gears 86 are each supported by one or even two axially successive needle bearings 85 on the planet axes 87, which are provided in bores of the planet carrier shaft 81, which has a centering bore 80. The planet carrier shaft 81 is mounted in the housing by means of the bearings 83, 84 and is sealed against it by means of the shaft sealing ring 82. The clamping nut 89 serves on its outer circumference as a running surface for the sealing lip of the shaft sealing ring. The housing also has a recess with a screw plug for filling or emptying the lubricant.

In FIG. 9, the planetary gear 9 is shown enlarged as a single part, this planetary gear having a flange block interface on the output side. In further exemplary embodiments according to the invention, this interface is designed as an industrial robot interface in accordance with the standard EN ISO 9409-1. The interface to the motor or adapter is again designed as an open fitting in the manner already mentioned. The pinion connected to the rotor shaft or adapter shaft, i.e. plug-in pinion or slip-on pinion, acts as the sun gear of the planetary gear after connection. Thermal expansion can be compensated with the room volume 97. The volume of the space advantageously has an axial extension to the sun gear of between 0.2 mm and 2 mm. The sun gear is in engagement with the planet gears 92 and is substantially determined in its position and orientation when connecting. The planet gears 92 are each supported by one or even two axially successive needle bearings 98 on the planet axles 91, which are provided in bores of the planet carrier shaft 95, which has a central bore which is sealed by means of a locking screw 96. In further exemplary embodiments according to the invention, the mentioned bore is designed as a threaded bore and the screw plug 96 has a corresponding thread. In FIG. 9, the screw plug 96 for filling or emptying the lubricant can be released and then reconnected. The planet carrier shaft 95 is mounted in the housing by means of the bearings 90 and sealed against it by means of the shaft sealing ring 94, the planet carrier 95 being machined on its outer circumference in a region such that it can be used as a running surface for the sealing lip of the shaft sealing ring.

FIG. 11 shows the assembly of the angular gear 7 with the adapter part 5 and adapter flange 11, the interface 74 being designed as an open fitting for adjusting the play between the spur gear 70 and the pinion 53. FIG. 12 shows the assembly of the planetary gear 8 with the adapter part 6 and adapter flange 11, the interface 74 being designed as an open fitting to compensate for tolerances. The planet gears 86 substantially determine the position and orientation of the pinion 69 used as a sun gear, in particular in a radial orientation.

FIG. 13 shows the assembly of the planetary gear 9 with the adapter part 6 and adapter flange 11, the interface 74 being designed as an open fitting to compensate for tolerances. The planet gears 92 substantially determine the position and orientation of the pinion 69 used as a sun gear, in particular in a radial orientation.

The invention thus enables connection of IEC standard motors by means of adapters or the manufacturer's own motors without an adapter to a gearbox, the manufacturer's motors being designed with a rotor shaft comprising an insertion or slip-on pinion. Thus, an extremely compact direct attachment to a gearbox is possible, but which can also be used with standard motors that can be connected via adapters.

Another advantage of the invention is that the adapters compensate for the thermal linear expansion of the rotor shaft and thus the transmission and the motor can be thermally decoupled by means of the adapters.

It is also essential that both single-stage or multi-stage transmissions with or without transverse force delivered on the input side, that is, transmissions with a driving spur gear stage or planetary gear stage, can be connected. Depending on the type of gearbox, the adapter can be designed with lateral force compensation, ie with adapter part 5, or without lateral force compensation, ie with adapter part 6. This results in a large number of possible variations.

The adapter also has the additional function of allowing the pinion to be centered when it is installed in the gearbox.

With the open fitting it is essential that radial displacements between the adapter and the gearbox are permitted before tightening the connecting screws, which are greater than corresponding displacements between the adapter and the motor. In further exemplary embodiments according to the invention, not only the entire angular gear has a play of less than 3 angular minutes, but also the planetary gear and also the two-stage planetary gear, which is formed from the planetary gear preliminary stage 10 and the planetary gear 9 or 8.

The motor with rotor 2 can thus also be designed as a direct-mounted motor (1, 2, 13) as well as another motor end shield 14, which then enables the connection to the transmissions 127, 128, 129, 130, 131 of FIG. 10, the motor end shield 14 can be connected to the adapter 126 or to the primary gear 125. A circled 1 is used in FIGS. 1 and 10 for the graphic representation of this connection possibility.

The reference number of the circled 2 shows that a direct attachment of the motor housing 1 together with the rotors 3 or 4 to the gears 127, 128, 129, 130, 131 is also possible. For this purpose, the motor housing 1 is therefore provided with an interface which corresponds to the interface of the gears mentioned.

This means that not only the standard gears 127, 128, 129, 130, 131 can be used for the motor housing, but also the servo gears 7,8,9.

The overall advantage for the invention is, among other things, that the number of parts in the geared motors is as small as possible, the reuse as large as possible within the modular system and the covered application variants as diverse as possible. In particular, both servo and standard geared motors are shown as variants.

The series is designed and constructed in such a way that all servo gear units in FIG. 1 only have integer ratios.

The same adapter is used in the variants according to FIG. 12 and FIG. 13. However, the planetary gear according to FIG. 13 is supported on both sides, the planetary gear according to FIG. 12 on one side, namely on the output side. Therefore, the adapter-side bearing 90 requires an axial length. This overall length is taken into account by means of the design and axial overall length of the adapter shaft 67 together with the insertion pinion 69 in such a way that the insertion pinion is completely inserted as a sun gear between the planet gears 92. In Figure 12 is the same adapter provided. So that the pinion 69 is fully inserted again between the planet gears 92 in this planetary gear, the housing 801 of the planetary gear is extended in such a way that the interface 74, i.e. the open fitting, is again in a corresponding axial position relative to the planet gears, as in FIG 3. As a result, an enlarged air volume is formed between the planet carrier shaft 81 and the open fitting in FIG. 12, which contributes to a reduction in air pressure when the temperature rises. This reduction in air pressure is particularly advantageous during assembly or when the temperature rises during operation. Overall, because of the goal of the largest possible combinatorics, an increased overall length in a variant of the series is accepted. Surprisingly, however, an advantage can be achieved overall, namely the reduction in air pressure when the temperature rises relative to a smaller overall volume of the transmission. This advantage is particularly important in the case of servo gear units, since high speeds can occur there during a positioning task, which can lead to corresponding heating. For this reason, the above-mentioned increase in overall length in the present series is surprisingly accepted consciously in order to achieve two advantages, firstly the combinatorial variety and secondly the reduction in air pressure.

The enlarged air volume can be clearly seen in FIG. 12 compared to FIG. If, instead of the adapter, a motor with an A-end shield is attached directly, the air volume is also formed in an analogous manner.

In further exemplary embodiments according to the invention, a single-stage hypoid gear is provided instead of the two-stage angular gear 7. It is advantageous that the translation number is an integer, even if the efficiency is slightly lower.

In the case of the direct attachment mentioned, it is particularly advantageous that no coupling is required and therefore the number of parts and thus also the costs are reduced. In addition, the design is therefore also compact.

The compensation of the thermal expansions takes place in FIG. 5 by means of the deformation of the metal bellows, in FIG. 6 by means of the displaceable bearings 65.

The angular gear 7 is always designed in such a way that it has an integral number of gear ratios, advantageously in the range from 3 to 30. To achieve the the gear parts are exchanged within one size; Depending on the desired gear ratio, a set comprising a gear wheel and hypoid pinion is exchanged for a second set comprising a gear wheel and a hypoid pinion. In addition, the spur gears of the input gear stage are varied in such a way that there is always an integer ratio overall. Varying the spur gears includes the helix angle and the profile shift with a constant center distance, i.e. within a respective size.

For the hypoid stage of the angular gear 7, the first sentence mentioned is advantageously designed for the ratio i = 3, the second sentence for the ratio i = 7.5.

The particularly advantageously generated gear ratios within one size, which cover the widest and densest possible range of gear ratios with as few different toothed parts as possible, are i = 3, 4, 6, 8, 10, 15, 20, 25, 30, 35 and 40 The translation numbers from i = 3 to 10 are generated using the hypoid sentence with i = 3 and the remaining translation numbers with the sentence with i = 7.5.

An advantageously designed series comprises 6 sizes, that is, 6 different center distances for the spur gear stage of the bevel gear 7. This number covers all industrially customary sizes or performance classes. In addition, an optimal ratio between the number of parts and the number of pieces can be achieved. In the case of even larger sizes, for example in the megawatt range or more, the number of pieces is so small that the advantage of multiple use of parts in different variants becomes small, but the conceptual disadvantages increase, for example the amount of material and thus also the material costs for the housing.

The sizes are designed in such a way that the maximum transferable torque of the sizes is graded in the manner M1 * (2 ^Λ (n-1)), where n is the size numbered from 1 to 6 and M1 is the maximum transferable torque of the smallest size, thus for n = 1.

In further embodiments according to the invention, deviations from said formula M1 ^* (2 ^Λ (n-1)) are advantageous if they are less than 18%. This has proven to be a particularly advantageous value. In other embodiments according to the invention, the value M1 = 40 Nm has proven to be particularly advantageous, since the above-mentioned advantageous part of the market for industrial gearboxes can thus be covered while maintaining the advantages mentioned.

In further embodiments according to the invention, values for M1 between 10 Nm and 100 nm have also proven to be advantageous.

In further embodiments according to the invention, the series comprises two types of low-backlash gearboxes, namely the gearboxes mentioned with 3 angular minutes and similar gearboxes, but which have 6 angular minutes. This means that more economical gears with 6 angular minutes and corresponding geared motors can be manufactured and offered.

LIST OF REFERENCE NUMBERS

1 motor housing

2 Rotor with cylindrical shaft end 5 3 Rotor with key for slip pinion

4 rotor for insert pinion

5 adapter part with two bearings

6 adapter part with one bearing

7 angular gear

10 8 planetary gear with cylindrical output shaft end

9 planetary gear units with flange block output

10 planetary gear pre-stage

11 adapter flange

12 Motor bearing plate with bearing 15 13 Motor bearing plate with bearing

14 engine end shield with bearing

21 center hole

22 rotor shaft

23 Motor bearing plate 20 24 interface

25 bearings

26 shaft seal

31 slip-on pinion

32 rotor shaft

25 33 Engine end shield

35 bearings

36 shaft seal

41 insert pinion

42 rotor shaft 30 45 bearings

46 shaft seal

50 clutch half on the gearbox side

51 center hole

52 Adapter shaft 35 53 slip-on pinion 54 shaft seal

55 bearings

56 Housing of the adapter part

57 bearings

5 58 Coupling half on the motor side

59 metal bellows

60 connecting screw

61 tension ring

62 adapter flange 10 63 slot

64 Housing of the adapter part

65 bearings

66 shaft seal

67 Adapter shaft 15 68 center hole

69 insert pinion

70 spur gear

71 bearings

72 sprockets

20 73 Face gear

74 open fitting

75 housing part

76 wave

80 center hole 25 81 planet carrier shaft

82 shaft seal

83 bearings

84 bearings

85 needle bearing 30 86 planet gear

87 planetary axis

88 room volume

89 clamping nut

90 bearings

35 91 planetary axis 92 planetary gear 93 housing

94 shaft seal

95 planet carriers

96 Screw plug 5 97 room volume

98 needle bearings

121 asynchronous motor

122 synchronous motor with square flange

123 asynchronous motor as servo motor 10 124 converter motor

125 primary gearbox

126 adapters

127 spur gear

128 parallel shaft gears

15 129 bevel gearboxes

130 worm gears

131 Spiroplan gear units

Claims

claims:

1. Kit for a series of geared motors, including gearboxes driven by electric motors,

characterized in that

at least for a subset of the variants within one size

the A-side motor bearing plate has an interface on the output side such that (iii) a transmission free of lateral force or (iv) a transmission free of non-lateral force can be connected directly,

wherein the direct connection takes place in such a way that the pinion is provided as a driving toothing part of the transmission.

2. Kit according to claim 1, characterized in that

the rotor shaft in the same housing 1 of the motor can be provided in at least two types of rotor shafts (3, 4),

- With the rotor shaft of the first type 3, a slip-on pinion is provided on the output side and

a plug-in pinion is provided on the output side of the rotor shaft of the second type 4,

3. Kit for a series of geared motors, including gearboxes driven by electric motors,

characterized in that

at least for a subset of the variants within one size

the A-side motor bearing plate has an interface on the output side such that (v) a transmission free of lateral force or (vi) a transmission free of non-lateral force can be connected directly,

the rotor shaft being provided with a toothing on the output side,

wherein the direct connection takes place in such a way that the rotor shaft is provided as a driving toothing part of the transmission.

4. Kit for a series of geared motors, including gearboxes driven by electric motors,

characterized in that

Within one size, the motor housing of the motor has an interface to the motor bearing plate on the output side such that at least two different variants of the motor bearing plate on the output side can be connected to the motor housing,

(i) wherein in a first variant 13 the A-side motor bearing plate has an interface on the output side such that the A-side motor bearing plate can be connected to an adapter flange 11 of an adapter,

the adapter comprising a first adapter part and the adapter flange 11,

the kit comprising at least two types (5, 6) of the first adapter part which can be connected to the adapter flange, the interface between the adapter flange 11 and the A-side motor end shield of the first variant comprising means for centering, such as fitting, the first adapter part in the first type 5

- With a non-transverse force-free transmission, such as a transmission with a spur gear stage arranged on the input side, by means of an interface comprising a two-dimensional open fitting, that is to say by means of displacements in one plane

Backlash setting of the non-overhung load-free interface, can be connected,

- includes an adapter shaft,

comprises at least two bearings and has first means for compensating axial expansions, in particular thermally induced expansions,

the first adapter part in the second type 6 being connectable to a shear-free gear, such as planetary gear, by means of an interface,

- includes an adapter shaft,

- Has second means for compensating axial expansions, in particular thermally induced expansions, and

- includes a warehouse,

(ii) in which, in a second variant 12, the A-side motor bearing plate has an interface on the output side such that a transmission free of lateral force and, alternatively, a non-lateral force transmission can be connected directly,

In the second variant, at least two types of rotor shafts (3, 4) can be provided for the same housing 1 of the motor,

wherein the direct connection takes place in such a way that the plug-in pinion or slip-on pinion is provided for engagement with at least one toothed part of the transmission.

5. Kit according to at least one of the preceding claims, characterized in that the output-side motor bearing plate comprises a bearing for the rotor shaft.

6. Kit according to at least one of the preceding claims, characterized in that

- In the rotor shaft of the first type 3, a slip-on pinion is provided on the output side and

7. Kit according to at least one of the preceding claims, characterized in that all gears have an open fitting as an interface on the input side.

8. Kit according to at least one of the preceding claims, characterized in that a Baig coupling is provided as the first means for compensating axial expansions.

9. Kit according to at least one of the preceding claims, characterized in that at least one roller and / or shim is provided as the second means for compensating axial expansions, in particular on a bearing of the adapter part.

10. Kit according to at least one of the preceding claims, characterized in that the gears of the series are designed with little play, in particular after adjusting the play by means of the displacements, that the play is less than 6 angular minutes per individual gear stage and / or gear overall.

11. Kit according to at least one of the preceding claims, characterized in that the transmissions of the series are designed with little play, in particular after adjusting the play by means of the displacements, that the play is less than 3 angular minutes per individual gear stage and / or gear overall.

12. Kit according to at least one of the preceding claims, characterized in that the lateral force-free, single-sided, connected to the adapter part 6 or to the A-end shield 12 of the motor gear 8 comprises a higher air volume for pressure compensation than the lateral force-free, bilaterally mounted, directly gear 9 connected to the adapter part 6 or to the A-end shield 12 of the motor.

13. Kit according to at least one of the preceding claims, characterized in that the transmission has a planetary gear stage as the driving stage.

14. Kit according to at least one of the preceding claims, characterized in that the non-transverse force-free gear is a two-stage gear, the gear stage arranged on the input side is designed as a spur gear stage, in particular with helical toothed gears.

15. Kit according to at least one of the preceding claims, characterized in that the second stage of the non-shear-free gear is an angular gear stage.

16. Kit according to at least one of the preceding claims, characterized in that the angular gear is designed in one stage, in particular as a hypoid gear.

17. Kit according to at least one of the preceding claims, characterized in that the gears are servo gears, in particular are therefore provided for precise positioning.

18. Kit according to at least one of the preceding claims, characterized in that in a third variant, the A-side motor end shield has an interface on the output side such that a standard gear, such as spur gear, parallel shaft gear, bevel gear or worm gear, can be connected.

19. Kit according to at least one of the preceding claims, characterized in that in the first variant the A-side motor end shield has an interface on the output side such that a primary gear or an adapter can be connected, which in turn can be connected to one of the standard gear units, such as spur gear units, Flat gear, bevel gear or worm gear, can be connected.

20. Kit according to at least one of the preceding claims, characterized in that the interface between the motor end shield and the adapter flange or between the adapter part and the gear are each designed as a square flange or as a round flange.

21. Kit according to at least one of the preceding claims, characterized in that at least one gear has a cylindrical shaft end on the output side.

22. Kit according to at least one of the preceding claims, characterized in that at least one transmission on the output side has a flange block interface according to the standard.

23. Kit according to at least one of the preceding claims, characterized in that the angular gear 7 is designed with a driving spur gear stage and at least one further angular gear stage such that it has an integral number of gear ratios.

24. Kit according to at least one of the preceding claims, characterized in that within a size in the angular gear stage depending on the desired

Gear ratio number one sentence, comprising wheel and pinion, is exchanged for a second sentence, comprising another wheel and another pinion.

25. Kit according to at least one of the preceding claims, characterized in that the wheel is a face gear and / or the pinion is a hypoid pinion. 5

26. Kit according to at least one of the preceding claims, characterized in that the angular gear stage has an axis offset.

10 27. Kit according to at least one of the preceding claims, characterized in that the translation numbers of the sentences behave as 1: 2.5.

28. Kit according to at least one of the preceding claims, 15 characterized in that the first sentence has the translation number 3.