DE102013003165A1 - Adapter system for connecting gear motor with gear units, has round recesses that are arranged in circumferential direction between each holes of gear box-side hole pattern and engine side hole pattern in adapters - Google Patents

Abstract

The adapter system has an adapter that is interposed between gear housing and a motor case, and is constructed as an integral ring element. A basic mounting ring portion of adapter is provided with a gear box-side hole pattern and an engine-side hole pattern respectively containing array of holes. Round recesses are arranged in circumferential direction between each hole of gear box-side hole pattern and immediately adjacent to hole on engine side hole pattern in adapters. Independent claims are included for the following: (1) a gear motor; (2) a gear motor series; and (3) a method for manufacturing gear motor of transmission module.

Description

The invention relates to an adapter system, a geared motor, a geared motor series and a manufacturing method for a geared motor.

From the DE 196 37 361 C2 is an adapter and adapter system for connecting motors with gears known, the number of adapter elements has been reduced compared to the previously known. The adapter has an adapter housing, in which an adapter shaft is supported by means of two bearings. The adapter shaft carries a pinion that meshes with the first gear of the transmission.

The "Manual gearboxes and gearmotors" Company publication by SEW Eurodrive from 07/2006 shows gearboxes which can be connected to three-phase motors by means of various adapters.

The DE 10 2011 013 918 A1 shows a coupling device with a driving and a driven shaft and a drive.

The DE 10 2008 017 643 A1 shows an adapter for a drive, comprising electric motor and gearbox.

The DE 10 2005 046 261 A1 shows a flange connection and a geared motor.

The DE 10 2008 048 530 A1 shows an adapter ring for connection between gearbox and engine.

The DE 102 46 391 A1 shows a hypoid reducing device for connecting a hypoid gear set with a motor.

The EP 0 567 048 A1 shows a two-part adapter for connecting a gearbox with a motor.

The invention is therefore the object of developing an adapter, a geared motor, a geared motor series and a manufacturing method for a geared motor, the environmental protection is improved.

According to the invention, the object in the adapter system according to the features specified in claim 1, wherein the geared motor according to the features specified in claim 13, in the geared motor series according to the features specified in claim 14 and in the manufacturing method for a geared motor according to the features specified in claim 16 solved.

Important features of the invention in the adapter system, comprising a gearbox, a motor and an adapter, in particular for connection of the gearbox to the engine, the adapter being interposable between the gearbox housing and the motor housing, are
the adapter is designed as a one-piece ring part,
the adapter having a base ring portion and a centering ring portion,
wherein the base ring portion has a gear-side hole pattern and a motor-side hole pattern,
wherein a respective hole pattern consists of a respective arrangement of bores,
wherein in each case a recess is arranged in the circumferential direction between each bore of the transmission-side hole pattern and each adjacent to this hole bore of the motor-side hole pattern in the adapter
wherein the respective recess is made out of round.

The advantage here is that a simple and stable connection of the transmission housing is made possible with the motor housing by means of the adapter. The integrally designed adapter can be produced in a simple manner as a casting. The recesses made in the adapter are particularly advantageous because a uniform wall thickness of the adapter can be produced by means of the recess. In the production by casting method thus a uniform curing is possible, so that production-related material defects such as voids are reduced. The reliability of the adapter system is thus improved.

In addition, by means of the recesses, the mass of the adapter can be reduced. So it is material saving, whereby the environment is protected.

By means of the centering ring portion of the adapter in a simple manner can be aligned to the transmission housing.

In an advantageous embodiment, at least one bore of the transmission-side hole pattern is arranged in the circumferential direction between each two holes of the motor-side hole pattern. The advantage here is that the holes are evenly distributed in the adapter can be arranged, whereby the mechanical stability of the adapter system is improved.

In an advantageous embodiment, at least one bore of the motor-side hole pattern is arranged in the circumferential direction between each two holes of the transmission-side hole pattern. The advantage here is that the holes are evenly distributed in the adapter can be arranged, whereby the mechanical stability of the adapter system is improved.

In an advantageous embodiment, the respective, in particular each, recess on the transmission side open, in particular wherein the respective recess in the axial direction is not continuous. The advantage here is that a recess open on one side can be produced in a simple manner by means of casting. In addition, the interior of the gear housing is sealed to the outside, so that penetration of dust and other impurities in the transmission can be prevented. So it is the reliability of the transmission can be improved.

In an advantageous embodiment, the respective recess extends in the circumferential direction of the base ring section further than in the radial direction. The advantage here is that the wall thickness in the adapter by means of the recesses is gleichmäßbar. The shape of the adapter can be adapted to the position of the holes.

In an advantageous embodiment, the respective recess widens with increasing radial distance in the circumferential direction, in particular wherein the respective recess is designed as a truncated pyramid with a trapezoidal base. The advantage here is that the adapter with the recess in a simple manner by casting method is manufacturable.

In an advantageous embodiment, the largest outer diameter of the Zentrierringabschnitts is smaller than the largest outer diameter of the base ring portion, in particular wherein the inner diameter of the Zentrierringabschnitts is less than or equal to the inner diameter of the base ring portion. The advantage here is that the centering ring is insertable into the gearbox flange. Advantageously, the gear flange has a recess into which the centering ring section can be introduced. Thus, the adapter by means of Zentrierringabschnitts and the recess in the gearbox flange to the gearbox flange is aligned.

In an advantageous embodiment, the bore center, in particular so the central axis of a respective bore of the transmission-side hole pattern is arranged at the same radial distance as the bore center of the engine-side hole pattern. The advantage here is that the adapter between a motor and a gearbox with the same flange diameter can be used. Thus, the adapter does not reduce the flange diameter but increases the axial distance between the engine and the transmission, so that a coupling for connecting a shaft of the transmission with a shaft of the motor can be arranged within the adapter axially overlapped by the adapter.

In an advantageous embodiment, the bore is a round bore, so that the rotational axis of symmetry of the round bore is parallel to the rotor shaft axis. The advantage here is that a round hole in a simple manner can be produced. The parallel alignment of the round holes to the rotor shaft axis allows additional stiffening of the adapter system by means of through the round holes passable screws.

In an advantageous embodiment, the Zentrierringabschnitt at least one interruption, wherein the interruption in the circumferential direction and in the axial direction is at least partially covered by the Beriech which is covered in the circumferential direction and in the axial direction of a through a bore, in particular a bore of the motor-side hole pattern , passed through screw, in particular from the screw head of the screw. The advantage here is that the adapter is compact executable. As a result, therefore, material can be saved, whereby the environmental protection can be improved.

In an advantageous embodiment of the angular distance between the centers of two next adjacent interruptions is equal to the angular distance between the bore centers of two holes of the engine-side hole pattern. The advantage here is that the adapter is compact executable. As a result, therefore, material can be saved, whereby the environmental protection can be improved.

In an advantageous embodiment, the base ring portion on an engine side ring portion and a gear side ring portion, wherein the gear side hole pattern is disposed in the gear side ring portion and the motor side hole pattern is disposed in the motor side ring portion, wherein the motor side ring portion is disposed radially inside of the transmission side ring portion. The advantage here is that the adapter is lightweight and compact executable. As a result, therefore, material can be saved, whereby the environmental protection can be improved.

In an advantageous embodiment, the centering ring section is arranged radially between the motor-side annular section and the gear-side annular section. The advantage here is that the adapter is lightweight and compact executable. As a result, therefore, material can be saved, whereby the environmental protection can be improved.

In an advantageous embodiment, the gearbox-side ring portion in the peripheral region of the interruption in the centering ring a radial recess, in particular a bulge, on. The advantage here is that a screw for connecting the adapter to the engine in a Bore in the radial region of the recess can be screwed. Advantageously, the recess is made large enough, so that the screw head is spaced from the ring portion.

In an advantageous embodiment, the largest inner diameter of the transmission-side ring portion in the peripheral region of the interruption is greater than the largest outer diameter of the centering ring. The advantage here is that the adapter is lightweight and compact executable. As a result, therefore, material can be saved, whereby the environmental protection can be improved.

In an advantageous embodiment, the adapter between the transmission housing and the motor housing can be interposed,
wherein the adapter has a gear-side hole pattern and a motor-side hole pattern,
in particular wherein a respective hole pattern consists of a respective geometric arrangement of bores.

The advantage here is that the adapter between the motor housing and the gear housing is inter-positionable and can be connected by means of screws screwed into the holes of the respective hole pattern. Thus, by means of the adapter, the motor housing of an engine and the transmission housing of a transmission can be connected to one another, in particular non-positively and / or positively by means of centering. In this case, the adapter allows the connection of motor and gearbox housings, which each have a different hole pattern. Thus, the compatibility of the engines and transmissions is improved, so that the environmental protection is improved.

• – in der Achse einer von dem Adapter radial zumindest teilweise umgebenen Kupplungshülse,
• – in der Achse einer Rotorwelle des Motors und/oder
• – in der Achse einer eintreibenden Welle des Getriebes

liegt, wobei die Bohrungen in dem Adapter, Getriebegehäuse und/oder dem Motorgehäuse angeordnet sind. Von Vorteil ist dabei, dass eine zentrierte Ausnehmung innerhalb des Adapters anordenbar ist, welche von dem die Bohrungen aufweisenden Wandungsabschnitt des Adapters umgeben ist.In an advantageous embodiment, each hole pattern comprises holes, wherein the holes are arranged on a circle, in particular its center

• In the axis of a coupling sleeve radially at least partially surrounded by the adapter,
• - In the axis of a rotor shaft of the motor and / or
• - In the axis of a driving shaft of the transmission

is located, wherein the holes in the adapter, transmission housing and / or the motor housing are arranged. The advantage here is that a centered recess can be arranged within the adapter, which is surrounded by the bores having wall portion of the adapter.

In an advantageous embodiment, the holes in the circumferential direction are spaced from each other, in particular regularly spaced from each other. The advantage here is that the force is distributed evenly over the entire circumference of the adapter when connecting the adapter to the engine and / or the transmission. Thus, the uniform introduction of a seal between the adapter and the engine and / or the transmission is simplified. In addition, the tightness of the seal is improved.

In an advantageous embodiment, the holes of the transmission-side hole pattern and the holes of the motor-side hole pattern in the circumferential direction are arranged alternately in the adapter. The advantage here is that both the motor housing and the gear housing with a uniform force distribution with the adapter can be connected. In particular, with an external force acting transversely to the axial direction of the adapter on the engine and / or the transmission, the resistance of the adapter connection is improved.

In an advantageous embodiment, a respective recess is arranged in the circumferential direction between each hole of the transmission-side hole pattern and each next adjacent hole of the motor-side hole pattern in the adapter. The advantage here is that the wall thickness of the adapter is uniform. In the production by means of a casting process, the formation of defects in the metal is reduced, such as voids. These defects are caused in particular by different solidification periods in components with thick and thin wall thicknesses. Thus, the durability of the adapter is improved and increased security. In addition, material can be saved, thus saving resources and the environment.

In an advantageous embodiment, the respective, in particular each, recess on the transmission side open, in particular wherein the respective recess in the axial direction is not continuous. The advantage here is that the adapter can be produced by means of a casting process and the stability of the adapter is increased.

In an advantageous embodiment, the bores of the transmission-side hole pattern are executed in the axial direction in a first wall portion of the adapter and the bores of the motor-side hole pattern are executed in the axial direction in a second wall portion of the adapter. The advantage here is that, in particular when the adapter is designed as Reduzierflansch, the wall sections have mutually different wall thicknesses. In particular, the wall thickness of the first wall section is greater than the wall thickness of the second wall section. Thus, the holes in the first wall portion as threaded holes, in particular threaded blind holes, executable. Through the holes in the second wall section connecting screws are passed. Due to the lower Wall thickness of the second wall portion, the screw heads of the connecting screws in the axial direction are completely retractable in the adapter. This saves material and protects the environment.

In an advantageous embodiment, the bore is a round bore, so that the rotational axis of symmetry of the round bore is parallel to the rotor shaft axis. The advantage here is that a round hole in a simple manner is manufacturable.

In an advantageous embodiment, the axial area covered by the second wall section at least partially covers the axial area covered by the first wall section. The advantage here is that the adapter flange is manufactured in one piece with low material costs.

In an advantageous embodiment, the transmission-side hole pattern has a greater maximum radial distance than the motor-side hole pattern, wherein the second wall portion is arranged at a smaller radial distance than the first wall portion, in particular wherein the maximum radial distance of the second wall portion is smaller than the maximum radial distance of the first wall portion. The advantage here is that a motor and a transmission, which differ in the radial distance of their hole pattern, are connected by means of the adapter.

In an advantageous embodiment, the adapter is connected to the motor housing by means of connecting screws, which have a screw head, wherein the smallest radial distance of the first wall section lies in the radial distance covered by the screw head. The advantage here is that the space in the interior of the adapter, which surrounds the clutch at least partially housing forming, is spacious executable. As a result, a collision of the coupling with the adapter is avoidable.

In an advantageous embodiment, the inner wall of the first Wandungsabschnitts radial recesses, in particular in the radial direction extending recesses, which cover an angular portion in the circumferential direction and are spaced from each other, so have a greater angular distance from each other than the amount of the angle section. The advantage here is that the adapter is compact executable. Thus, material is saving.

In an advantageous embodiment, the maximum radial distance of the transmission-side hole pattern is smaller than the maximum radial distance of the motor-side hole pattern, wherein the first wall portion is arranged radially further inboard than the second wall portion. The advantage here is that a motor and a transmission, which differ in the radial distance of their hole pattern, are connected by means of the adapter.

In an advantageous embodiment, the second wall section is formed from a plurality of subsections. In particular, the subsections are spaced apart in the circumferential direction, in particular wherein the subsections in the axial and in the radial direction overlap a region which is also covered by the first wall section in each case. The outer wall of the first wall section preferably has at least one trapezoidal radial recess, in particular so that the vertical projection of the radial recess into a plane whose normal is directed in the axial direction is a trapezoid. The advantage here is that the adapter is compact executable, so that material can be saved.

• – ein Getriebegehäuse,
• – ein Motorgehäuse,
• – eine eintreibende Welle, welche im Getriebegehäuse mittels eines motorseitigen Lagers gelagert ist, und
• – einen Adapter mit einem getriebeseitigen Lochbild,

insbesondere wobei der Adapter zwischen dem Getriebegehäuse und dem Motorgehäuse angeordnet ist,
sind, dass ein Quotient d/R kleiner als 0,6 ist, insbesondere kleiner ist als 0,4,
wobei d der Innendurchmesser des motorseitigen Lagers ist,
wobei R der maximale Radialabstand des getriebeseitigen Lochbildes zur Rotorwellenachse ist.Important features of the invention in the geared motor, comprising

• A transmission housing,
• A motor housing,
• - An input shaft, which is mounted in the gear housing by means of a motor-side bearing, and
• An adapter with a gear-side hole pattern,

in particular, wherein the adapter is arranged between the transmission housing and the motor housing,
are that a quotient d / R is less than 0.6, in particular less than 0.4,
where d is the inner diameter of the engine-side bearing,
where R is the maximum radial distance of the gear-side hole pattern to the rotor shaft axis.

The advantage here is that a geared motor, for which d / R is less than 0.6, with particularly small bearings executable, which are inexpensive. Thus, an oversized flange on the transmission is present, so that the transmission with different sized motors is connectable. Therefore, the same transmission is used twice or more times in a geared motor series. In this way, a high variance can be achieved in the series with a low number of parts.

• – zumindest einen Adapter mit einem getriebeseitigen Lochbild,
• – zumindest einen Motor mit einem Motorgehäuse und einer darin gelagerten Rotorwelle,
• – zumindest ein erstes und zweites Getriebe mit jeweils einer eintreibenden Welle, welche mittels jeweils eines motorseitigen Lagers in einem jeweiligen Getriebegehäuse gelagert ist und
• – zumindest eine Kupplung zur Verbindung der Rotorwelle des Motors und der eintreibenden Welle des Getriebes,

umfasst,
insbesondere wobei der Adapter zwischen Motor und Getriebe angeordnet ist, wobei das Getriebegehäuse ein zum getriebeseitigen Lochbild des Adapters entsprechendes Lochbild aufweist, so dass eine Schraubverbindung ausführbar ist,
wobei das erste und zweite Getriebe sich unterscheiden in dem Innendurchmesser des motorseitigen Lagers der eintreibenden Welle des Getriebes,
sind, dass
das getriebeseitige Lochbild eines oder des Adapters für zumindest die beiden Getriebe, insbesondere also erstes und zweites Getriebe, gleich ist.Important features of the invention in the geared motor series whose variants can be produced and / or manufactured from a modular system,
being the construction kit

• At least one adapter with a gear-side hole pattern,
• At least one motor with a motor housing and a rotor shaft mounted therein,
• - At least a first and second gear, each having a driving shaft, which is mounted in each case by means of a respective engine-side bearing in a respective gear housing and
• At least one coupling for connecting the rotor shaft of the motor and the driving shaft of the gearbox,

includes,
in particular wherein the adapter is arranged between the engine and the transmission, wherein the transmission housing has a hole pattern corresponding to the transmission side hole pattern of the adapter, so that a screw connection can be executed,
wherein the first and second gears differ in the inner diameter of the engine-side bearing of the driving shaft of the transmission,
are that
the gear-side hole pattern of one or the adapter for at least the two transmissions, in particular so first and second gear, is the same.

The advantage here is that a geared motor series is possible, with a large variety of variants with low number of components, in particular, the number of adapters required can be reduced. The adapter can be selected independently of the gearbox since the gearbox side hole pattern of the adapter is the same for all gearboxes. In particular, therefore, the hole pattern of the gear flange is identical for all transmissions.

In a further advantageous embodiment, the two gears differ in the respective quotient d / R, where d is the inner diameter of the respective motor-side bearing, where R is the maximum radial distance of the respective gear-side hole pattern to the rotor shaft axis, in particular wherein the quotient d / R is less than 0.6, in particular wherein the quotient d / R is less than 0.4. The advantage here is that in the kit gearbox with a large variance of bearing inner diameters are used. In this case, gearboxes with a small bearing inner diameter have a small nominal torque of, for example, less than or equal to 50 Nm. Gearboxes with a large inner bearing diameter have a large nominal torque of, for example, greater than or equal to 400 Nm. In particular, the adapter is independent of the bearing inner diameter selectable.

In a further advantageous embodiment, the kit has a plurality of adapters having different motor-side hole patterns, so that different motors are connectable, wherein the gear-side hole pattern of the adapter is the same. The advantage here is that a greater variance of engines and a greater variance of gears in the kit can be used compared to the number of adapters required. Thus, the required storage for adapters is also low.

In a further advantageous embodiment, the coupling is surrounded by the adapter at least partially housing forming. The advantage here is that the adapter and the coupling are executed independently, in particular are multi-piece and do not touch. The coupling is protected by means of the at least partially housing-forming adapter from environmental influences. Thus, the reliability of the clutch is increased.

In a further advantageous embodiment, the coupling has a coupling sleeve, wherein the coupling sleeve is surrounded by the adapter at least partially housing forming. The advantage here is that the coupling rotates freely with the coupling sleeve within the adapter. Thus, no additional adapter is required for receiving the coupling and / or the coupling sleeve.

In a further advantageous embodiment, the maximum outer diameter of the coupling sleeve is greater than the minimum inner diameter of the adapter. The advantage here is that the adapter is compact. Thus, the geared motor assembled from the transmission, the motor and the adapter is also compact. As a result, the geared motor is versatile, especially in applications that allow little space for the geared motor.

In a further advantageous embodiment, the first wall section has at least one recess, wherein the recess narrows with increasing radial distance in the circumferential direction. The advantage here is that the recess and the radial recess can be arranged overlapping in the circumferential direction. Thus, the adapter is compact executable. Preferably, the adapter has a uniform wall thickness.

In a further advantageous embodiment, the area axially covered by the adapter and the area axially covered by the coupling partially overlap, wherein the coupling is radially spaced from the adapter. The advantage here is that the adapter increases the axial distance between the engine and the transmission, so that the coupling between the engine and transmission can be arranged. Thus, the clutch is usable for a variety of engines, since no additional space in the motor housing for the clutch is required. In addition, the adapter is inexpensive to produce, since no additional bearings for the clutch are required.

In a further advantageous embodiment, the coupling has the coupling sleeve and a Clutch hub part, wherein the coupling sleeve rotatably, in particular form-fitting manner, in particular by means of a curved toothing, is connected to the coupling hub part. The advantage here is that the rotor shaft and the driving shaft can be connected by means of the coupling. The coupling is designed so that a small axial offset can be compensated by means of the coupling.

In a further advantageous embodiment, the coupling sleeve is non-rotatably, in particular form-fitting, connected to the rotor shaft of the motor, in particular wherein the coupling hub part rotatably, in particular form-fitting, is connected to the driving shaft of the transmission. The advantage here is that the rotor shaft and the driving shaft can be connected by means of the coupling.

In a further advantageous embodiment, the coupling sleeve receives the coupling hub part, in particular in an axially directed recess of the coupling sleeve, and / or wherein the coupling sleeve, the coupling hub part axially at least partially covered and / or wherein the coupling sleeve radially overlaps the coupling hub. The advantage here is that the adapter is compact executable and inexpensive to produce.

In an advantageous embodiment, the connection region between the coupling sleeve and the coupling hub part is axially spaced from the axially covered region of the adapter. The advantage here is that the adapter is compact executable and inexpensive to produce.

In a further advantageous embodiment, the maximum outer radius of the coupling sleeve tapers toward the engine, in particular wherein the radial extent of the free space between the coupling sleeve and the adapter increases toward the engine. The advantage here is that the clearance improves the reliability of the geared motor, since the rotating parts are spaced apart from the adapter, in particular screws are spaced, which are screwed through holes in the adapter in the engine.

• – zumindest einen Adapter mit einem getriebeseitigen Lochbild,
• – zumindest einen Motor mit einem Motorgehäuse und einer darin gelagerten Rotorwelle,
• – zumindest ein erstes und zweites Getriebe mit jeweils einer eintreibenden Welle, welche mittels jeweils eines motorseitigen Lagers in einem jeweiligen Getriebegehäuse gelagert ist und
• – zumindest eine Kupplung zur Verbindung der Rotorwelle des Motors und der eintreibenden Welle des Getriebes,

umfasst,
sind, dass
wahlweise eine erste oder zweite Variante hergestellt wird,
wobei die erste Variante aus dem ersten Getriebe, dem Motor, dem Adapter und der Kupplung gebildet wird,
wobei die zweite Variante aus dem zweiten Getriebe, dem Motor, dem Adapter und der Kupplung gebildet wird,
wobei der in der ersten Variante verwendete Adapter und der in der zweiten Variante verwendete Adapter gleich, insbesondere identisch, sind,
wobei der Innendurchmesser des motorseitigen Lagers des ersten Getriebes unterschiedlich ist zum Innendurchmesser des motorseitigen Lagers des zweiten Getriebes,
insbesondere wobei das zur Verbindung verwendete getriebeseitige Lochbild eines oder des Adapters für zumindest die beiden Getriebe, insbesondere also erstes und zweites Getriebe, gleich ist.Important features of the invention of the manufacturing method for a geared motor from a gearbox,
the gearbox

• At least one adapter with a gear-side hole pattern,
• At least one motor with a motor housing and a rotor shaft mounted therein,
• - At least a first and second gear, each having a driving shaft, which is mounted in each case by means of a respective engine-side bearing in a respective gear housing and
• At least one coupling for connecting the rotor shaft of the motor and the driving shaft of the gearbox,

includes,
are that
optionally a first or second variant is produced,
wherein the first variant is formed by the first gearbox, the engine, the adapter and the clutch,
wherein the second variant is formed of the second transmission, the engine, the adapter and the clutch,
wherein the adapter used in the first variant and the adapter used in the second variant are the same, in particular identical,
wherein the inner diameter of the engine-side bearing of the first gear is different from the inner diameter of the engine-side bearing of the second gear,
in particular wherein the transmission-side hole pattern used for the connection of one or the adapter is the same for at least the two transmissions, in particular therefore the first and second transmissions.

The advantage here is that an adapter for different geared motor variants is used. Thus, a high variety of variants is possible with a small number of parts in the kit. As a result, in particular, the cost of storage is low, whereby the storage costs are reduced.

In an advantageous embodiment of the coupling, the driving shaft is connected to a coupling sleeve, in particular by means of feather key connection, wherein the aborting shaft is connected to a coupling hub part, in particular by means of feather key connection,
wherein the coupling hub part has an outer toothing and the coupling sleeve has an inner toothing, wherein the toothings are engaged with one another, wherein on the coupling hub part a feather key for positive connection with the driven shaft is integrally formed, in particular integrally with the outer toothing of the coupling hub part. The advantage here is that the one-piece design only a few parts are needed and thus the environment is protected. In addition, by the use of sintered material and / or plastic a small clearance of the clutch can be achieved and thus a low noise. Also in this way the environment is spared because the sound emissions are reducible. Furthermore, the reduced play and the reduced rattling due to the lower moments of inertia, the life of the arrangement renewable and thus in turn reduced resource consumption and the environment spared.

In an advantageous embodiment, the driving shaft has a keyway, in particular an extending in the axial direction of the keyway, in which a feather key is arranged, which has in a corresponding keyway for positive connection with the coupling sleeve. The advantage here is that a simple low-cost and low-play keyway connection can be used, whereby the environment is protected.

In an advantageous embodiment, the driving shaft is non-positively connected to the coupling sleeve, in particular pressed with a press fit into the coupling sleeve,
in particular, wherein the region covered axially by the non-positive connection comprises or at least partially encompasses the axial region covered by the feather key connection. The advantage here is that the axial play is reduced or even brought to disappear by means of frictional connection, in particular press connection in the region of the keyway of the driving shaft with the coupling sleeve. The driving shaft is preferably made of steel. Thus, a well-fitting press connection with a plastic coupling sleeve can be produced in a simple manner.

In an advantageous embodiment, a feather key is integrally formed on the coupling hub portion for positive connection with the driven shaft. The advantage here is that the environment is protected by the reduced number of parts, the game of feather key is reduced and thus the noise is reduced, whereby the environment is again protected by means of the reduced noise emissions.

In an advantageous embodiment, the coupling hub part together with integrally formed key is made of sintered material, in particular of sintered metal,
in particular wherein the external toothing is also formed integrally with the key. The advantage here is that a particularly simple cost-effective and resource-saving production of the coupling hub part is effected. In addition, the moment of inertia is reduced compared to metallic solid material and thus in turn protects the environment.

In an advantageous embodiment, the coupling sleeve is formed of plastic, in particular wherein the internal toothing is also integrally formed with the remaining coupling sleeve, in particular produced in the plastic injection molding process. The advantage here is that a particularly cost-effective and resource-saving production process can be used.

In an advantageous embodiment, a hollow region is arranged around the foot region of the radially inwardly extending integrally formed on the coupling hub part formed around feather, which extends in the radial direction of at least 10% or at least 20% of the radial length of the feather key. The advantage here is that the notch effect and wear on edges of the driven shaft can be reduced.

In an advantageous embodiment, a circlip for axially limiting the Kupplungsnabenteils is provided, in particular in a circumferentially extending groove of the aborting shaft. The advantage here is that an axial fuse can be executed in a simple manner.

In an advantageous embodiment, the driving shaft has a shaft step as an axial boundary for the coupling sleeve, in particular wherein the shaft step is arranged on the side facing away from the coupling hub side of the coupling sleeve. The advantage here is that an axial limitation is made possible in a simple manner.

In an advantageous embodiment, the coupling sleeve is axially delimited on the side facing the driving shaft by a shaft step of the driving shaft and on the other axial side by the coupling hub part,
and or
the coupling hub part is axially bounded on the side facing away from the driving shaft side of a shaft stage of the driven shaft and on the other axial side of the coupling sleeve. The advantage here is that only one shaft stage must be provided on the driving and aborting shaft, and thus both coupling parts, so the coupling hub part and the coupling sleeve, are axially limited.

In an advantageous embodiment, a center hole is arranged on a front side of the driving shaft and / or on an end face of the driven shaft for reducing the moment of inertia. The advantage here is that the mass is reduced and thus the game is reduced. Therefore, the noise and wear is reduced and the service life extended.

In an advantageous embodiment of a drive with an aforementioned coupling device, the driving shaft is a rotor shaft of an electric motor and the driven shaft connected to the driving toothing part of the transmission shaft, in particular pinion shaft, wherein the driving shaft has a shaft step as axial Has limitation of the coupling sleeve, in particular wherein at the shaft stage, the coupling sleeve rests with its axial end region. The advantage here is that a cost-effective axial limitation is achieved.

In an advantageous embodiment, the driving shaft is supported by means of a bearing which is accommodated in a housing part, in particular of the motor. The advantage here is that the coupling device requires no storage of clutch shaft parts.

In an advantageous embodiment, the aborting shaft is supported by means of a bearing, which is accommodated in a housing part, in particular of the transmission. The advantage here is that the coupling device requires no storage of clutch shaft parts.

In an advantageous embodiment, an adapter flange is arranged between the bearing housing receiving housing parts, in particular wherein the housing parts are detachably connected to the adapter flange, in particular by means of connecting screws,
in particular wherein in each case at least one centering means, in particular centering collar, is arranged on the adapter flange and / or on the housing parts receiving the bearing. The advantage here is that two different interfaces are created axially on both sides by means of the adapter, so that different gearboxes are connected to each same engine and different engines to each same gear together. Thus, a high variance in the series with few components can be achieved.

Further advantages emerge from the subclaims. The invention is not limited to the combination of features of the claims. For the skilled person, further meaningful combination options of claims and / or individual claim features and / or features of the description and / or figures, in particular from the task and / or the task posing by comparison with the prior art arise.

The invention will now be explained in more detail with reference to schematic illustrations:
In the 1 is a gear coupling, comprising a coupling hub part 1 and a coupling sleeve 3 , shown in exploded view.

In the 2 is a cross section through the clutch shown installed between the engine and transmission state. In this case, the rotor shaft and the motor flange are shown hatched together, although the rotor shaft is rotatably mounted relative to the motor flange and the motor housing.

In the 3 is a cross section through the coupling hub part 1 shown.

In the 4 an associated plan view is shown.

In the 5 is an enlarged section of 4 shown.

6 shows an overview of various geared motors of the transmission system according to the invention, each comprising a transmission 74 . 740 . 741 , which is designed as an angle gear, an adapter according to the invention and a motor 68 . 680 . 681 . 682 , The geared motors are arranged in a table in the figure. Each line shows gearmotors with one motor each 68 . 680 . 681 . 682 the same size and the matching same adapter 22 . 80 . 81 . 226 and each different gears 74 . 740 . 741 , Each column shows geared motors with one gearbox each 74 . 740 . 741 same size and different motors 68 . 680 . 681 . 682 ,

In the 7 to 10 individual geared motors are shown in sectional view, comprising a transmission 74 with a nominal torque of 90 Nm, which is designed as an angle gear, various inventive adapter, in particular adapter flanges 22 . 80 . 81 . 226 and different engines 68 . 680 . 681 . 682 ,

It shows 7 a geared motor with an adapter flange 226 in sectional view, bringing a motor 68 with 0.12 kW or 0.18 kW rated power and a connection flange 67 with 90 mm diameter to the gearbox 74 can be cultivated.

8th shows a geared motor with an adapter flange 80 in sectional view, bringing a motor 680 with 0.25 kW or 0.37 kW rated power and a connection flange 67 with 105 mm diameter to the gearbox 74 can be cultivated.

9 shows a geared motor with an adapter flange 22 in sectional view, being a motor 681 with 0.55 kW or 0.75 kW rated power and a connection flange 67 with 120 mm diameter to the gearbox 74 can be cultivated.

10 shows a geared motor with an adapter flange 81 in sectional view, bringing a motor 682 with 1.1 kW rated power and a connection flange 67 with 140 mm diameter to the gearbox 74 can be cultivated.

In the 11 and 12 geared motors are shown in sectional view, comprising various gears 740 . 741 , which are designed as angular gear, each with an adapter flange 22 what a motor 681 with 0.55 kW rated power and a connection flange 67 with 120 mm diameter to the gearbox 740 . 741 can be cultivated.

It shows 11 a geared motor with an adapter flange 22 for the installation of a gearbox 740 with a nominal torque of 50 Nm to the engine 681 in sectional view.

12 shows a geared motor with an adapter flange 22 for the installation of a gearbox 741 with a nominal torque of 180 Nm to the engine 681 in sectional view.

13 shows an overview of various geared motors of the transmission system according to the invention, each comprising a transmission 115 . 1151 . 1152 . 1153 , which is designed as a spur gear, an adapter, in particular adapter flange 22 . 80 . 81 . 226 . 246 , and a motor 68 . 680 . 681 . 682 . 683 , The geared motors are arranged in a table in the figure. Each line shows gearmotors with one motor each 68 . 680 . 681 . 682 . 683 the same size and the matching same adapter 22 . 80 . 81 . 226 . 246 and each different gears 115 . 1151 . 1152 . 1153 , Each column shows geared motors with one gearbox each 115 . 1151 . 1152 . 1153 same size and different motors 68 . 680 . 681 . 682 . 683 ,

In the 14 to 18 individual geared motors are shown in sectional view, comprising a transmission 74 with a nominal torque of 200 Nm, which is designed as a spur gear, various adapter flanges 22 . 80 . 81 . 226 . 246 and different engines 68 . 680 . 681 . 682 . 683 ,

It shows 14 a geared motor with an adapter flange 226 in sectional view, bringing a motor 68 with 0.12 kW or 0.18 kW rated power and a connection flange 67 with 90 mm diameter to the gearbox 74 can be cultivated.

15 shows a geared motor with an adapter flange 80 in sectional view, bringing a motor 680 with 0.25 kW or 0.37 kW rated power and a connection flange 67 with 105 mm diameter to the gearbox 74 can be cultivated.

16 shows a geared motor with an adapter flange 22 in sectional view, bringing a motor 681 with 0.55 kW or 0.75 kW rated power and a connection flange 67 with 120 mm diameter to the gearbox 74 can be cultivated.

17 shows a geared motor with an adapter flange 81 in sectional view, bringing a motor 682 with 1.1 kW or 1.5 kW rated power and a connection flange 67 with 140 mm diameter to the gearbox 74 can be cultivated.

18 shows a geared motor with an adapter flange 246 in sectional view, bringing a motor 683 with 2.2 kW or 3 kW rated power and a connection flange 67 with 160 mm diameter to the gearbox 74 can be cultivated.

In the 19 to 21 geared motors are shown in sectional view, comprising various gears 115 . 1151 . 1152 . 1153 , which are designed as a spur gear, each with an adapter flange 22 for the cultivation of an engine 68 with 0.55 kW or 0.75 kW rated power and a connection flange 67 with 120 mm diameter.

It shows 19 a geared motor with an adapter flange 22 for the installation of a gearbox 1151 with a nominal torque of 50 Nm to the engine 681 in sectional view.

20 shows a geared motor with an adapter flange 22 for the installation of a gearbox 1152 with a nominal torque of 85 Nm to the engine 68 in sectional view.

21 shows a geared motor with an adapter flange 22 for the installation of a gearbox 1153 with a nominal torque of 400 Nm to the engine 68 in sectional view.

22 shows an adapter flange 226 for a gear motor with holes 220 for connecting screws 78 in an oblique view, wherein the diameter of the connecting flange 67 of the motor 68 . 680 smaller than the diameter of the gearbox flange 23 ,

23 shows an adapter flange 22 for a gear motor with holes 220 for connecting screws 78 in an oblique view, wherein the diameter of the connecting flange 67 of the motor 681 the same size as the diameter of the gearbox flange 23 ,

24 shows an adapter flange 246 for a gear motor with holes 220 for connecting screws 78 in an oblique view, wherein the diameter of the connecting flange 67 of the motor 683 greater than the diameter of the gearbox flange 23 ,

The coupling hub part 1 is made of a sintered metal. Thus, it has a low mass and the moment of inertia of the clutch is small, whereby the noise is reduced, especially when changing direction, and the dynamics of the clutch is increased.

At the coupling hub part 1 is a feather key 2 integrally formed. Thus, the game is reduced and reduces the noise, especially when changing direction.

The feather key 2 is on the wall of a centrally located recess of the coupling hub part 1 arranged. In this case, the feather key protrudes radially inward, wherein the transition region has such a radially outwardly arranged and so small radius that, after insertion of the shaft to be connected by means of the key, the one clutch shaft section 77 having a corresponding keyway, a cavity 40 it is present at the foot of the section of the coupling hub part projecting into the recess as a keyway area 1 ,

A hollow area 40 remains even after insertion of the aborting shaft, in particular thus a driving shaft of the transmission, in particular pinion shaft, in the coupling hub part 1 exist and thus reduces the contact surface between the driven shaft and the coupling hub part 1 , In addition, the moment of inertia is reduced.

The coupling hub part 1 has an external toothing, which is in engagement with an internal toothing of the coupling sleeve for torque transmission.

The coupling sleeve 3 has a first axial section, the toothed section 6 , on, in which the internal toothing is arranged.

The axial direction is the axial direction of the rotor shaft 20 of the motor 68 . 680 . 681 . 682 . 683 ,

In a second axial section, the connecting section 5 , In turn, a recess is arranged, on whose wall a keyway 4 is arranged.

In this case, the maximum outer radius of the first axial section is greater than the maximum outer radius of the second axial section. The maximum outer radius of the coupling sleeve 3 tapers to the engine 68 . 680 . 681 . 682 . 683 in particular, wherein the radial extent of a free space 27 between the coupling sleeve 3 and the adapter flange 22 . 226 . 236 . 246 to the engine 68 . 680 . 681 . 682 . 683 increases.

The open space 27 between the adapter flange 22 . 226 . 236 . 246 and the coupling sleeve 3 is filled with air and / or a lubricant such as gear oil. The open space 27 extends in the axial direction from the motor flange to a sealing ring 66 , In this free space 27 is the coupling with the coupling sleeve 3 and the coupling hub part 1 , the rotor shaft 20 and the driving wave 77 arranged as rotating parts of the transmission.

The open space 27 So it is radially inside the adapter flange 22 . 226 . 236 . 246 arranged. Here is the free space 27 Oil-tight, so the rotating parts are protected from dirt and dust.

The driving shaft, in particular rotor shaft 20 , Is designed as a solid shaft and has a keyway into which a feather key is inserted into the keyway 4 protrudes.

The coupling sleeve 3 is designed in its internal toothing area with an involute toothing. Accordingly, the external teeth of the coupling hub part 1 crowned executed.

The aborting shaft is a solid shaft and has a keyway into which the feather key 2 is introduced.

Here is the abortive wave 114 or pinion shaft 63 coaxially arranged to the rotor shaft 20 ,

At the axial end face of the aborting shaft is a center hole 25 arranged. Thus, the moment of inertia is reduced.

The coupling sleeve 3 is axially limited by one on the rotor shaft 20 trained wave level 21 , In addition, the rotor shaft 20 pressed into the connecting section 5 , This interference fit also causes axial securing in the axial direction away from the motor.

There is also a circlip 24 arranged on the driven shaft for axially limiting the driven shaft on the coupling hub part 1 ,

The gearbox flange 23 is with the adapter flange 22 by means of connecting screws 26 connected.

The coupling hub part 1 has said external teeth in a first axial section. On the external teeth, the torque is transmitted. The area of the recess of the coupling hub part 1 in which the feather key 2 integrated molded, and the feather key 2 extend axially on both sides beyond the axial region of the external teeth. In 3 is this extended receiving section with reference numerals 30 designated. On its outer contour is a radius R2, which reduces the notch effects, mounted between the axial portion of the external toothing and the axial end portion.

The axial securing of the coupling sleeve 3 is by inserting a grub screw 69 , which is preferably radially aligned, can be improved. The grub screw 69 connects the coupling sleeve 3 and the rotor shaft 20 , by itself form-fitting with the coupling sleeve 3 is connected, in particular at least partially disposed in a recess thereof, and by pressing on the rotor shaft produces a frictional connection.

In an alternative embodiment of the invention is on the grub screw 69 for axial securing and the circlip 24 to secure the coupling hub part 1 waived. Instead, the coupling part 1 and the coupling sleeve 3 extends axially so that only a very small air gap is provided between them, which is less than 2 mm or less than 1 mm, in particular less than 0.5 mm. Thus, the two parts limit each other axially. Because on the engine side facing the coupling sleeve 3 from the wave level 21 axially limited and on the output side is the coupling hub part 1 limited by a wave level of the local wave. Thus, when the two parts move towards each other, the two face each other, are mutually parallel end surfaces of the parts having the axial direction as their normal direction. As a result, a mutual axial securing of the two coupling parts in both directions is thus achieved in a simple manner and the axial securing by the securing ring can be dispensed with. In an advantageous embodiment, this shortens the overall length, thus saving material and protects the environment.

The adapter flange 22 . 226 . 236 . 246 is arranged radially outside the clutch and spaced in the radial direction of the clutch. The coupling sleeve overlaps 3 and the adapter flange 22 . 226 . 236 . 246 in the axial direction at least partially.

The coupling sleeve 3 is non-rotatable and form-fitting by means of a curved toothing with the coupling hub part 1 connected. The coupling sleeve covers the coupling hub part axially. Here is the connection area of the coupling hub part 1 with the coupling sleeve 3 axially spaced from that of the adapter flange 22 . 226 . 236 . 246 arranged axially covered area.

The coupling sleeve 3 is non-rotatable with a rotor shaft 22 of the motor 68 . 680 . 681 . 682 . 683 connected and the coupling hub part 1 is non-rotatable with a driving shaft 77 of the transmission 74 . 115 . 740 . 741 . 1151 . 1152 . 1153 connected.

The in 7 shown geared motor has a transmission 74 with a Spiroplanverzahnung on. The spiroplan gearing is characterized by a spiroplane wheel and a pinion shaft 63 , wherein the toothing section 64 of the spiroplane wheel with the gear section 76 the pinion shaft 63 combs. Under Spiroplanrad is understood here a face wheel 72 , whose front side has a radially inner planar portion and a radially outer toothing portion 64 having. This gearing section 64 is formed such that the tooth flank shape has a curved course or is designed as Kronradverzahnung. The axis of the planer wheel 72 and the axis of the pinion shaft 63 are perpendicular to each other, with an axial offset between the axes of 30% to 70% of the radius of the face gear 72 is provided, preferably the axial offset is 50% to 60% of the radius of the face wheel 72 , Thus, the illustrated transmission 74 an angular gear.

The gear 74 is arranged in a housing, wherein the housing has a first housing part 62 which is substantially cuboidal. In this first housing part 62 are arranged: the plan wheel 72 , the pinion shaft 63 , a warehouse 60 and another camp 65 with a snap ring 70 and a sealing ring 66 , A roof surface of the first housing part 62 is open for mounting the components. By means of a second housing part 75 , which acts as a lid, and screws, not shown, which thread in not shown threaded holes in the first housing part 62 can be screwed, this mounting hole is closed. In this case, a seal, not shown, between the first and second housing part 62 and 75 arranged.

Instead of a screw is also a threaded pin with a nut usable.

A first end face of the first housing part 62 has a protuberance, wherein in this protuberance the bearing 65 with the snap ring 70 and the sealing ring 66 is arranged. The protuberance is arranged on the motor side. The protuberance has a circular recess parallel to the first end surface. Surrounding this recess is the gear flange 23 arranged, wherein the recess radially centered in the transmission flange 23 is arranged.

The gear flange juts 23 in the axial direction over the protuberance, so that the transmission flange 23 for all in the 6 and 13 shown gear 74 . 740 . 741 . 115 . 1151 . 1152 . 1153 having the same outer diameter. Here, the outer diameter of the gear flange 23 in particular, regardless of the size of the transmission 74 . 740 . 741 . 115 . 1151 . 1152 . 1153 , Preferably, this outer diameter is 120 mm. This uniformity makes a modular system possible, since every gearbox 74 . 740 . 741 . 115 . 1151 . 1152 . 1153 to every configuration of the adapter flange 22 is flanged.

In the case of in 11 shown smallest transmission 740 with 50 Nm nominal torque is the gearbox flange 23 So clearly oversized. In contrast, the in 21 illustrated largest transmission 1153 with 400 Nm nominal torque a gearbox flange 23 with a very small diameter in relation to the gearbox dimensions.

The pinion shaft 63 is by means of a first camp 65 and a second camp 60 in the first housing part 62 of the transmission 74 stored. This is the first camp 65 on the engine 68 facing the end of the pinion shaft 63 arranged and the second camp 60 is at the engine 68 remote end of the pinion shaft 63 arranged. The pinion shaft 63 points to the engine 68 facing away from a center hole 61 to reduce the moment of inertia of the pinion shaft 63 , On the engine 68 facing side opens the pinion shaft 63 in a clutch shaft section.

Furthermore, the pinion shaft 63 a gear section 76 on, wherein the toothing section 76 is interposed between a wheel axle and the first bearing 65 , Wheel axle is understood here as the axis of rotation of the Spiroplan wheel. Furthermore, the toothed section meshes 76 the pinion shaft 63 with the toothing section 64 of the spiroplane wheel. On the engine 68 facing side of the first bearing 65 indicates the pinion shaft 63 a clutch shaft section 77 on.

In particular, the pinion shaft 63 with the toothing section 76 and the clutch shaft portion 77 made in one piece. The coupling shaft section 77 protrudes into the gearbox flange 23 into it. Here is the coupling shaft section 77 positively connected to the coupling hub part 1 the adapter by means of a keyway connection.

The pinion shaft 63 and the face wheel 72 are made of metal, especially steel. In particular, the face wheel 72 made of nodular cast iron GGG60 and the pinion shaft 63 is made of tempered steel or surface hardened case steel. In particular, the tempered steel has a tensile strength of 600 to 800 N / mm ² . In particular, the case hardening steel has a hardness of HV1 600 to 800, in particular of HV1 680 to 780, preferably of HV1 720 or HV0.5 720.

In particular, 16MnCr5 is suitable as case-hardened steel. For larger dimensions, other steels are suitable, in particular 15CrNi6 or 17CrNiMo6.

The lubricant used is one with a high EP activation based on polyglycol or polyalphaolefin. In particular, a lubricant is used, which is classified with respect to its Fresragagfähigkeit in class GL5 of the API classification.

Motor side of the first bearing 65 is a snap ring 70 arranged, this snap ring 70 downstream is a sealing ring 66 , Thus, a leakage is in the transmission 74 arranged lubricant in particular transmission oil from the transmission 74 prevented. This is the transmission 74 independent of the adapter flange 226 and the engine 68 ready to ship and ready for transport and storage. In the case of a transmission defect so is a stored in place gearbox 74 easy to grow and the flanged engine 68 is still usable. Thus, there is no reconfiguration of control of the engine 68 required with complex commissioning process.

The plan wheel 72 is non-rotatable with a shaft 71 connected. This is a centered circular recess with a keyway 73 provided in the crown wheel. This feather keyway 73 is positively connected by means of a key, not shown, with the shaft 71 connected. The wave 71 is by means of two bearings, not shown, in the first housing part 62 stored. The one from the gearbox 74 opposite axial end portion of the shaft 71 is rotatably connected to an application, not shown. In particular, the wave 71 executed as a solid shaft. An unillustrated sealing ring seals the housing to the shaft 71 outwards. Thus, the inside of the transmission 74 Protected against the penetration of dust particles from the environment.

In further embodiments of the invention, a hollow shaft can be used instead of the solid shaft. Here, the shaft has a continuous keyway 73 on, which is designed as a longitudinal groove. By means of this longitudinal groove is an application to be driven directly to the transmission 74 rotatably connected, in particular form-fitting connectable.

The in 7 shown geared motor has a motor 68 with one compared to the uniform diameter of the gearbox flange 23 smaller connection flange 67 in particular, the flange diameter of the motor is 68 only 90 mm compared to the standard gearbox flange 23 with 120 mm diameter. The adapter flange used 226 So it is designed as a reducing flange. For this purpose, the adapter flange tapers 226 radially in the axial direction to the engine 68 out. It has a first axial portion of the adapter flange 226 a very low degree of taper from 0 ° to a maximum of 10 °. In this first axial section of the adapter flange 22 is a hole 220 , In particular a blind bore with internal thread, arranged for receiving connecting screws 26 by means of which the transmission 74 connected to the adapter. A second axial section of the adapter flange directly adjoining the first axial section 226 has a stronger degree of tapering from 40 ° to 70 °, which leads to the connection flange 67 of the motor 68 flattens out. In this case, the axial length of the first axial portion of the adapter flange 226 about 40% to 60% of the axial length of the second axial portion of the adapter flange 226 ,

22 shows the in 7 illustrated adapter flange 226 in an oblique view of a transmission-side end face of the adapter flange 226 , In the adapter flange 226 is a hole 220 arranged in a second wall section. Here is the second wall section at the engine 68 facing end face of the adapter flange 226 arranged. In the in 22 the embodiment shown, the second wall portion is radially inward to a first wall portion of the adapter flange 22 arranged. The first wall section connects the engine 68 with the gearbox 74 , In particular, the first wall section touches the engine 68 and the gearbox 74 , Through a hole 230 in the second wall section is a connecting screw 78 hindurchführbar, which in a threaded blind hole in the engine 68 can be screwed in to connect the adapter flange 226 with the engine 68 ,

In this case, the first wall portion extends axially from the transmission-side end portion of the bore 220 to the engine-side end of the bore 220 , The second wall portion extends axially from the transmission-side end portion of the bore 230 to the engine-side end of the bore 230 , The holes 220 and the holes 230 extend in the axial direction through the adapter flange 22 . 226 . 246 therethrough.

The first wall section extends at the adapter flange 226 in the radial direction of a cylindrical outer wall of the adapter flange 226 over the holes 220 and the recesses 221 up to a step in the inner wall of the adapter flange 226 , Here are the holes 230 arranged on the stage radially opposite side of the stage.

The second wall section of the adapter flange 226 extends in the radial direction of the centered recess 222 in the adapter flange 226 over the holes 230 up to the step in the inner wall of the adapter flange 226 ,

The inner wall of the adapter flange 226 thus has a level. In this case, the section of the inner wall with the smallest diameter is cylindrical. The diameter of the inner wall increases in the axial direction to the transmission stepwise. In a further section of the inner wall with a larger diameter, the inner wall has recesses. In this case, the diameter of the inner bore in the region of the recess in a radial angle range of the adapter flange 226 increased. The maximum inner diameter in the area of all wells is the same size. In the circumferential direction between the recesses, the inner wall has a constant diameter.

The second wall section thus protrudes in the region of the recesses into the first wall section. The axial thickness is thus smaller in the region of the depressions than the axial thickness of the first wall section.

The adapter flange 22 . 226 . 246 is preferably produced by means of a casting process.

A hole pattern of the gearbox flange 23 has at least three axial bores, which are circular in the end face of the gearbox flange 23 are arranged. Preferably, four holes in the circumferential direction are regularly spaced from each other at the end face of the transmission flange 23 arranged.

Under hole image is understood, a geometric arrangement of holes, in particular holes, in a plane. In particular, the maximum radial distance of the hole pattern of the radial distance of the hole of the hole pattern with the largest distance to the rotor shaft axis.

A quotient d / R, formed from a radial distance R of the holes of the hole pattern of the transmission to the rotation axis as a divisor and the inner diameter d of the bearing 65 as a dividend, varies for different sizes of the gearbox 74 . 740 . 741 . 115 . 1151 . 1152 . 1153 , This quotient is less than 0.6 and for smaller sizes even less than 0.4. Thus, smaller size gearboxes have a significantly oversized gearbox flange 23 on.

The size of a gearbox describes its structural size and / or the associated nominal torque in Nm. A large size gearbox is thus structurally larger than a small size gearbox and / or has a larger nominal torque.

The motor 68 has a motor housing with the connection flange 67 on. The in this connection flange 67 arranged axial bores 230 form a hole pattern of the engine. This hole pattern is on one end face of the connection flange 67 arranged. Preferably, four holes in the circumferential direction are regularly spaced from each other at the end face of the connecting flange 67 arranged.

The adapter flange 22 . 226 . 246 has a gear-side hole pattern and a motor-side hole pattern. The gear-side hole pattern is at least partially identical to the hole pattern of the transmission. The engine-side hole pattern is at least partially identical to the hole pattern of the engine. Preferably, the holes 220 the gear-side hole pattern designed essentially as threaded holes, in particular designed as threaded blind holes. The holes 230 the motor-side hole pattern are designed as continuous holes, in particular which have no thread.

Preferably, the holes 220 the gearbox side hole pattern and the holes 230 the motor-side hole pattern alternately in the adapter flange 22 . 226 . 246 arranged. It is in the circumferential direction between a hole 220 the transmission-side hole pattern and the next adjacent in the circumferential direction bore 230 the motor-side hole pattern each have a recess 221 . 231 . 241 arranged. This recess 221 is preferably on the transmission-side end face of the adapter flange 22 open. Thus, the recess is not made consistently.

At the in 22 illustrated adapter flange 226 is the radial distance of the holes 220 the transmission-side hole pattern, in particular the radial distance to the rotor shaft axis of the motor 68 , greater than the radial distance of the holes 230 the motor-side hole pattern, in particular the radial distance to the rotor shaft axis of the motor 68 ,

In this case, the transmission-side hole pattern in a transmission-side ring section 223 the adapter flange 226 arranged. The motor-side hole pattern is in a motor-side ring section 224 the adapter flange 226 arranged. The motor-side ring section 224 is thus radially inward of the transmission-side ring section 223 arranged.

The axial thickness of the motor-side ring portion 224 is smaller than the axial thickness of the gear-side ring portion 223 , Preferably, the thickness of the motor-side ring portion 224 less than 30% of the thickness of the transmission-side ring portion 223 ,

The transmission-side ring section 223 extends in the axial direction from the motor housing to the transmission housing. The motor-side ring section 224 touches the motor housing, it is spaced from the gear housing.

Radial between the motor-side ring section 224 and the transmission-side ring portion 223 is a centering ring section 225 arranged. The centering ring section 225 has interruptions. In the circumferential direction and in the axial direction, the interruptions are at least partially covered by a screw head. Here is the screw head having connecting screw 78 passed through a bore of the motor-side hole pattern.

The angular distance between the centers of two nearest adjacent interruptions is equal to the angular distance between the bore centers of two holes of the engine-side hole pattern.

The axial thickness of the centering ring section 225 is larger than the axial thickness of the gear-side ring portion 223 , The centering ring section 225 cantilevers from the adapter flange on the gearbox side 226 out. Thus, the centering ring section is suitable 225 for aligning the adapter flange 226 to the gearbox flange 23 ,

The adapter flange 226 is by means of the connecting screw 78 with the engine 68 connected. When assembling the gear motor, the connecting screw 78 from the inside of the adapter flange 226 through the hole 230 in the motor-side ring section 224 the adapter flange 226 into a threaded hole in the connecting flange 67 of the motor 68 screwed. Then the coupling sleeve 3 on the rotor shaft 20 inserted and by means of the grub screw 69 screwed. The coupling hub part 1 becomes with the clutch shaft section 77 of the transmission 74 connected by a feather key connection. Finally, the transmission 74 with the adapter flange 226 connected by the coupling hub part 1 in the coupling sleeve 3 is pushed and a connecting screw 26 through a recess in the gearbox flange 23 into a hole 220 , in particular threaded blind bore in the adapter flange 226 is screwed.

Alternatively, it is also an engine 68 with continuous holes in the connection flange 67 mountable. This is the connecting screw 26 through the hole 230 in the motor-side ring section 224 the adapter flange 226 and through the hole in the connection flange 67 led the engine and bolted with a nut.

The adapter flange 22 . 226 . 246 is annular with a radially centered circular recess 222 executed. It has radially arranged recesses 221 . 231 . 241 on which the transmission side are open and motor side and radially inward and radially are closed on the outside. These recesses 221 . 231 . 241 are advantageous in the manufacture of the adapter flange 22 . 226 . 246 by casting process. The adapter flange 22 . 226 . 246 has sections with different wall thickness, which solidify at different speeds during casting and thereby form voids. At voids preferentially arise material defects. Thus, a uniform wall thickness by means of recesses 221 . 231 . 241 advantageous in the sections with large wall thickness.

8th shows a geared motor with a motor 680 with a larger connection flange 67 , in particular, its diameter is 105 mm. This is the connection flange 67 of the motor 68 smaller than the gearbox flange 23 with 120 mm, but the connection flange 67 is bigger than the one in 7 shown connection flange 67 , This indicates the adapter flange 80 for this embodiment, another form: on to the transmission flange 23 adjacent first axial section, which measures a maximum of 20% of the axial length of the adapter flange, has a low degree of taper of 0 ° to 10 °. In addition to the first axial portion, a second axial portion is arranged whose length is about 60% to 90% of the axial length of the adapter flange 80 is. The degree of taper of this second axial section is between 10 ° and 30 °. Between the connection flange 67 of the motor 68 and the second portion of the adapter flange 80 a third axial section is interposed, whose length is at most 20% of the axial length of the adapter flange 80 is. The third axial section again has a low degree of taper of 0 ° to 10 °.

The in 9 shown geared motor has a motor 681 on with one in comparison to the gearbox flange 23 equal connection flange 67 , The diameter of the connection flange 67 of the motor 681 and gearbox flange 23 is therefore 120 mm each. In this embodiment, therefore, no reduction of the flange diameter by means of an adapter is required. Nevertheless, an adapter flange 22 used, the required for the installation of the clutch axial distance between engine 681 and gear 74 causes. Furthermore, in this adapter flange 22 Recesses arranged to receive at one end of the engine 681 arranged centering bolt 90 , The motor 681 is by means of connecting screws 78 with the adapter flange 22 connected.

23 shows the in 9 illustrated adapter flange 22 in an oblique view of the transmission-side end face of the adapter flange 22 , In this further embodiment of the invention the adapter flange 22 this has a base ring section 232 on. It is in the axial direction of the adapter flange 22 a hole 230 executed for receiving a connecting screw 78 , in particular, the hole 230 designed as a round bore. The hole 230 has two axial sections in the axial direction. The first axial section on the gear-facing side of the adapter flange has a diameter which is greater than the diameter of the head of the connecting screw 78 , in particular 5% to 30% larger than the diameter of the head of the connecting screw 78 , Thus, the connecting screw 78 completely feasible through the first axial section. A second axial section of the bore 230 is arranged on the motor side of the first axial section. The second axial portion has a smaller diameter than the first axial portion, so that the thread of the connecting screw 78 can be passed through the second axial section. Here is the diameter of the head of the connecting screw 78 greater than the diameter of the second axial portion of the bore 230 , In particular, the diameter of the second axial section is 20% to 30% smaller than the diameter of the head of the connecting screw 78 ,

Radially inward of the base ring section 232 is a centering ring section 235 arranged. In this case, the axial thickness of the centering ring section 235 greater than the axial thickness of the base ring portion 232 , The centering ring section 235 cantilevers from the adapter flange on the gearbox side 22 out. Thus, the centering ring section is suitable 235 for aligning the adapter flange 236 to the gearbox flange 23 ,

The further embodiment according to 23 thus shows an adapter flange 22 with a transmission-side and a motor-side hole pattern, wherein the radial distance of the transmission-side hole pattern to the rotation axis is equal to the radial distance of the motor-side hole pattern to the rotation axis. Thus, the in 23 illustrated adapter flange 22 designed as a straight flange.

10 shows a geared motor with a motor 682 with a larger connection flange 67 as the gearbox flange 23 , in particular, the diameter of the connecting flange 67 of the motor 68 140 mm compared to 120 mm diameter on gearbox flange 23 , In this embodiment, therefore, a reduction of the flange diameter of the engine 67 to the gearbox 74 by means of the adapter flange 81 required. For this purpose, the adapter flange 81 three axial sections: the one to the engine 67 adjacent first axial section has a very small radial taper in axial direction to the gearbox 74 from 0 ° to 10 °, the axial length of the first axial section is a maximum of 20% of the total axial length of the adapter flange. Next to the first axial section of the adapter flange 81 a second axial section is arranged, which has a degree of taper of 10 ° to 30 °. This second axial section extends over 60% to 90% of the axial length of the adapter flange 81 ,

Between the transmission 74 and the second axial portion of the adapter flange 81 is a third axial section of the adapter flange 81 interposed. This third axial section has a very low degree of taper in the axial direction of the transmission 74 from 0 ° to 10 °. The axial length of the third axial section is at most 20% of the axial length of the adapter flange 81 , Furthermore, in this adapter flange 81 Recesses arranged to receive centering pins arranged on the motor side 90 , The motor 682 is by means of a connecting screw 78 with the adapter flange 81 connected.

The in 14 shown geared motor has a gearbox 115 with spur gear teeth on. The transmission has a first housing part 116 which is essentially cuboid and whose roof surface is open for installation of internal components of the transmission 115 , A second housing part 113 , which is designed as a lid, closes the open roof surface of the first housing part. This will be a screw 112 through a recess in the second housing part 113 in a threaded blind bore in the first housing part 116 screwed. Between the first housing part 116 and the second housing part 113 is arranged a seal, not shown.

At the bottom of the gearbox 115 is a pedestal 104 arranged, in particular, where the stand 104 Holes for receiving screws for mounting the transmission 115 on the ground.

The engine side is on the gearbox 115 a gearbox flange 23 arranged. This gear flange 23 has at least one recess through which a connecting screw 26 is hindurchführbar and in a bore 220 , in particular threaded blind hole in the adapter flange 226 is screwed to the connection of the transmission 115 with the adapter flange 226 ,

On the gearbox flange 23 opposite side of the transmission 115 is a wave 109 arranged, which is designed as a solid shaft and has a keyway. By means of a feather key 110 is the wave 109 connectable with a arranged in a hollow shaft keyway of an application, not shown.

In a further embodiment of the invention, the application has a solid shaft, which is connectable by means of another adapter, not shown, with the shaft 109 of the transmission 115 ,

The wave 109 is by means of a first camp 106 and a second camp 102 in the first housing part 116 stored. This is the first camp 106 on the application side in the first housing part 116 arranged. The first camp 106 and the wave 109 be by means of a sealing ring 108 sealed on the application side to the outside. Between the sealing ring 108 and the camp 106 is a snap ring 107 interposed to fix the shaft 109 in the first housing part 116 ,

The second camp 102 is at the engine end of the shaft 109 in the interior of the first housing part 116 arranged. Between the first and second camp 106 and 102 are a spacer ring 111 and a bike 103 on the wave 109 arranged, with the spacer ring 111 next to the first camp 106 is arranged and the wheel 103 is interposed between the second camp 102 and the spacer ring 111 ,

The wheel 103 meshes with a pinion toothing, not shown, which is arranged on a second shaft, not shown, and by means of two bearings, not shown, in the interior of the housing 116 of the transmission 115 is stored. The second wave also has a wheel 101 on, which with a pinion gear of a driving shaft 114 combs. The pinion toothing is integral with the driving shaft 114 executed, in particular, the pinion teeth in the driving shaft 114 milled.

In further embodiments of the invention, as in 18 shown, the pinion gear is a pinion gear part 180 executed. Thus, the wave 114 with the pinion gear part 180 designed in two pieces, wherein the pinion gear part 180 by means of a feather key 181 positively connected to the driving shaft 114 ,

The driving wave 114 is by means of two bearings 100 and 65 in the first housing part 116 stored. This is the camp 65 axially between the bearing 100 and the clutch shaft portion 77 arranged. The warehouse 65 is by means of a snap ring 70 fixed. Axial between the bearing 100 and the camp 65 is a sealing ring 66 arranged, which the interior of the first housing part 116 to the rotor shaft 20 seals off.

The driving wave 114 opens motor side in a clutch shaft section 77 , which one as described above with the coupling hub part 1 connected is.

The gear 115 So it is designed as a two-stage spur gear.

In further embodiments of the invention, as in 19 is shown on the application side, a flange 190 with the first housing part 116 of the transmission 1151 by means of a screw 192 connected. This is in the flange 190 arranged a recess, not shown, in particular a round bore through which the screw 192 can be passed in a thread blind hole, not shown, in the first housing part 116 ,

By means of the flange 190 An application is connectable with the geared motor. For this purpose, at least one not shown recess in the flange 190 arranged through which a screw 191 can be passed.

In further embodiments of the invention, as in 18 is a geared motor with a motor 683 with an even larger connection flange 67 as the in 10 illustrated connection flange 67 with the gearbox 115 connected. In particular, the diameter of the connection flange 67 of the motor 683 160 mm compared to 120 mm diameter on the gearbox flange 23 , In this embodiment, therefore, a greater reduction of the flange diameter of the engine 683 to the gearbox 115 by means of the adapter flange 246 required. For this purpose, the adapter flange 246 three axial sections: the one to the engine 683 adjacent first axial portion has a very small degree of radial taper in the axial direction of the transmission 115 from 0 ° to 10 °, the axial length of the first axial section is a maximum of 20% of the total axial length of the adapter flange 246 , Next to the first axial section of the adapter flange 246 a second axial section is arranged, which has a degree of taper of 20 ° to 40 °. This second axial section extends over 60% to 90% of the axial length of the adapter flange 246 , Between the transmission 115 and the second axial portion of the adapter flange 246 is a third axial section of the adapter flange 246 interposed. This third axial section has a very low degree of taper in the axial direction of the transmission 74 from 0 ° to 10 °. The axial length of the third axial section is at most 20% of the axial length of the adapter flange 246 , Furthermore, in this adapter flange 246 Recesses arranged to receive centering pins arranged on the motor side 90 , The motor 683 is by means of a connecting screw 78 with the adapter flange 246 connected.

24 shows the in 18 shown adapter flange in an oblique view of the transmission-side end face of the adapter flange 246 , In this further embodiment of the invention the adapter flange 246 is the second wall section 244 formed from several subsections. In particular, wherein the sections are circumferentially spaced from each other.

In particular, the subsections of the second wall section 244 as at least one radial well 240 radially outward of the first wall portion 243 the adapter flange 246 executed. This recess is as a substantially tetrahedral recess in the outer wall of the first wall portion 243 executed the adapter flange. In this case, one surface of the tetrahedron is parallel to the motor-side end side of the adapter flange 246 arranged. This area has the second hole 230 to carry out a connecting screw 78 into a threaded blind hole in the engine 683 can be screwed in to fix the adapter flange 246 at the engine 683 ,

The further embodiment according to 24 thus shows an adapter flange 246 with a gear-side and a motor-side hole pattern, wherein the radial distance of the transmission-side hole pattern to the rotation axis is smaller than the radial distance of the motor-side hole pattern to the rotation axis.

Radially inside the first wall section 243 is a centering ring section 245 arranged. In this case, the axial thickness of the centering ring section 245 greater than the axial thickness of the first wall portion 243 , The centering ring section 245 cantilevers from the adapter flange on the gearbox side 246 out. Thus, the centering ring section is suitable 245 for aligning the adapter flange 246 to the gearbox flange 23 ,

The axial thickness of the second wall section 244 is less than 30% of the axial thickness of the first wall portion 243 , Here is the second wall section 244 formed of several sections, preferably, the second wall section 244 formed of four sections. In particular, these sections are not directly contiguous. In each of these sections is a hole 230 the motor-side hole pattern arranged. In this case, each subsection is a trapezoidal recess in the outer wall of the first wall section 243 executed.

LIST OF REFERENCE NUMBERS

1

Clutch hub portion

2

Key, integrally formed on the coupling hub part 1

3

coupling sleeve

4

keyway

5

connecting portion

6

toothed section

20

rotor shaft

21

wave level

22

adapter flange

23

gearbox

24

circlip

25

Zentner hole

26

connecting screw

27

free space

30

receiving portion

40

hollow area

60

camp

61

centering

62

housing part

63

pinion shaft

64

toothed section

65

camp

66

seal

67

flange

68

engine

69

grub screw

70

snap ring

71

wave

72

crown gear

73

keyway

74

transmission

75

housing part

76

toothed section

77

Clutch shaft section

78

connecting screw

80

adapter flange

81

adapter flange

90

Zentner bolts

100

camp

101

wheel

102

camp

103

wheel

104

stand

105

projection

106

camp

107

snap ring

108

seal

109

wave

110

Adjusting spring

111

spacer tube

112

screw

113

housing part

114

wave

115

transmission

116

housing part

180

Pinion toothing part

181

Adjusting spring

190

flange

191

screw

192

screw

220

drilling

221

recess

222

recess

223

ring section

224

ring section

225

Zentrierringabschnitt

226

adapter flange

230

drilling

231

recess

232

Basic ring section

235

Zentrierringabschnitt

240

radial depression

241

recess

243

wall section

244

wall section

245

Zentrierringabschnitt

246

adapter flange

680

engine

681

engine

682

engine

683

engine

740

transmission

741

transmission

1151

transmission

1152

transmission

1153

transmission

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 19637361 C2 [0002]
• DE 102011013918 A1 [0004]
• DE 102008017643 A1 [0005]
• DE 102005046261 A1 [0006]
• DE 102008048530 A1 [0007]
• DE 10246391 A1 [0008]
• EP 0567048 A1 [0009]

Cited non-patent literature

• "Manual gearboxes and gearmotors" Company publication by SEW Eurodrive from 07/2006 [0003]

Claims (16)

Adapter system comprising a transmission ( 74 ), a motor ( 68 ) and an adapter, in particular for connection of the transmission ( 74 ) with the engine ( 68 ), wherein the adapter is interposed between the transmission housing and the motor housing, characterized in that the adapter is designed as a one-piece ring part, wherein the adapter has a base ring portion ( 232 ) and a centering ring section ( 225 . 235 ), wherein the base ring section ( 232 ) has a gear-side hole pattern and a motor-side hole pattern, wherein a respective hole pattern from a respective arrangement of holes ( 220 . 230 ), wherein in the circumferential direction between each bore ( 220 ) of the gear-side hole pattern and each to this hole ( 220 ) Next adjacent hole ( 230 ) of the motor-side hole pattern in the adapter in each case a recess ( 221 . 231 . 241 ) is arranged, wherein the respective recess ( 221 . 231 . 241 ) is executed out of round, in particular wherein in the circumferential direction between two holes ( 230 ) of the motor-side hole pattern at least one bore ( 220 ) of the gear-side hole pattern is arranged or being in the circumferential direction between two holes ( 220 ) of the gear-side hole pattern at least one bore ( 230 ) of the motor-side hole pattern is arranged, in particular wherein the holes ( 220 ) of the gear-side hole pattern and the holes ( 230 ) of the motor-side hole pattern in the circumferential direction are arranged alternately in the adapter. Adapter system according to at least one of the preceding claims, characterized in that the respective, in particular each, recess ( 221 . 231 . 241 ) is open on the transmission side, in particular wherein the respective recess ( 221 . 231 . 241 ) is not continuous in the axial direction, in particular wherein the respective recess ( 221 . 231 ) widened in the circumferential direction with increasing radial distance, in particular wherein the respective recess ( 221 . 231 ) is designed as a truncated pyramid with a trapezoidal base surface, in particular wherein the normal of the base surface is aligned in the axial direction, and / or that the respective recess ( 221 . 231 . 241 ) in the circumferential direction of the base ring section ( 232 ) extends further than in the radial direction, in particular wherein the respective recess ( 221 . 231 . 241 ) widened in the circumferential direction with increasing radial distance, in particular wherein the respective recess ( 221 . 231 . 241 ) is designed as a truncated pyramid with a trapezoidal base, in particular wherein the normal of the base is aligned in the axial direction. Adapter system according to at least one of the preceding claims, characterized in that the largest outer diameter of the Zentrierringabschnitts ( 225 . 235 ) is smaller than the largest outer diameter of the base ring section ( 232 ), in particular wherein the inner diameter of the centering ring section ( 225 . 235 ) smaller than or equal to the inner diameter of the base ring section ( 232 ), and / or that the bore center, in particular therefore the center axis, of a respective bore ( 220 ) of the gear-side hole pattern is arranged at the same radial distance as the bore center of the motor-side hole pattern, and / or that the bore ( 220 . 230 ) is a round bore, so that the rotational axis of symmetry of the round bore is parallel to the rotor shaft axis. Adapter system according to at least one of the preceding claims, characterized in that the centering ring section ( 225 ) has at least one interruption, wherein the interruption in the circumferential direction and in the axial direction is at least partially covered by the Beriech, which is covered in the circumferential direction and in the axial direction of a through a bore ( 230 ), in particular a bore of the engine-side hole pattern ( 230 ), in particular the screw head of the screw, in particular wherein the angular distance between the centers of two nearest adjacent interruptions equal to the angular distance between the bore centers of two holes ( 230 ) of the motor-side hole pattern is. Adapter system according to at least one of the preceding claims, characterized in that the base ring section ( 232 ) a motor-side ring section ( 224 ) and a transmission-side ring section ( 223 ), wherein the gear-side hole pattern in the transmission-side ring portion ( 223 ) is arranged and the motor-side hole pattern in the motor-side ring portion ( 224 ), wherein the motor-side ring portion ( 224 ) radially within the transmission-side ring portion ( 223 ), in particular wherein the centering ring section ( 225 ) radially between the motor-side ring portion ( 224 ) and the transmission-side ring section ( 223 ) is arranged. Adapter system according to at least one of the preceding claims, characterized in that the transmission-side ring section ( 223 ) in the peripheral region of the interruption in the centering ring section ( 225 ) has a radial recess, in particular a bulge, in particular wherein the largest inner diameter of the transmission-side ring portion ( 223 ) in the peripheral region of the interruption is greater than the largest outer diameter of the centering ring. Adapter system according to at least one of the preceding claims, characterized in that each hole pattern bores ( 220 . 230 ), the bores ( 220 . 230 ) are arranged on a circle, in particular its center - in the axis of a radially at least partially surrounded by the adapter coupling sleeve ( 3 ), - in the axis of a rotor shaft ( 20 ) of the motor ( 68 ) and / or - in the axis of a driving shaft of the transmission ( 74 ), whereby the holes ( 220 . 230 ) are arranged in the adapter, transmission housing and / or the motor housing, in particular wherein the bores ( 220 . 230 ) are spaced apart in the circumferential direction, in particular regularly spaced from each other, in particular wherein the bores ( 220 ) of the gear-side hole pattern and the holes ( 230 ) of the motor-side hole pattern in the circumferential direction are arranged alternately in the adapter. Adapter system according to at least one of the preceding claims, characterized in that the adapter system has a coupling, wherein the axially overlapped by the adapter portion and the axial overlapping of the clutch area overlap, wherein the coupling is radially spaced from the adapter, in particular wherein the Clutch the coupling sleeve ( 3 ) and a coupling hub part ( 1 ), wherein the coupling sleeve ( 3 ) rotatably, in particular form-fitting, in particular by means of a curved toothing, with the coupling hub part ( 1 ), in particular wherein the coupling sleeve ( 3 ) rotatably, in particular form-fitting, with the rotor shaft ( 20 ) of the motor ( 681 ), in particular wherein the coupling hub part ( 1 ) rotatably with the driving shaft of the transmission ( 74 ), in particular wherein the coupling sleeve ( 3 ) the coupling hub part ( 1 ), in particular in an axially directed recess of the coupling sleeve ( 3 ), and / or wherein the coupling sleeve ( 3 ) the coupling hub part ( 1 ) axially at least partially covered and / or wherein the coupling sleeve ( 3 ) the coupling hub part ( 1 ) radially overlapped, in particular wherein the connection region between the coupling sleeve ( 3 ) and the coupling hub part ( 1 ) is axially spaced from the axially covered region of the adapter, in particular wherein the maximum outer radius of the coupling sleeve ( 3 ) to the engine ( 681 ), in particular wherein the radial extent of the free space 27 between the coupling sleeve ( 3 ) and the adapter to the engine ( 681 ) increases. Adapter system according to at least one of the preceding claims, characterized in that the bores ( 220 ) of the gear-side hole pattern in the axial direction in a first wall portion ( 243 ) of the adapter are executed and the holes ( 230 ) of the motor-side hole pattern in the axial direction in a second wall section ( 244 ) of the adapter are executed, and / or that of the second wall section ( 244 ) covered axial region at least partially from the first wall section ( 243 Covered axial area covered. Adapter system according to at least one of the preceding claims, characterized in that the gear-side hole pattern has a greater maximum radial distance than the motor-side hole pattern, wherein the second wall portion ( 244 ) is arranged at a smaller radial distance than the first wall section ( 243 ), in particular wherein the maximum radial distance of the second wall section ( 244 ) is smaller than the maximum radial distance of the first wall section ( 243 ). Adapter system according to at least one of the preceding claims, characterized in that the adapter with the motor housing by means of connecting screws ( 78 ), which have a screw head, wherein the smallest radial distance of the first wall portion ( 243 ) lies in the radial distance range covered by the screw head, in particular wherein the inner wall of the first wall portion ( 243 ) has radial recesses, in particular in the radial direction extending recesses, which cover an angular portion in the circumferential direction and are spaced from each other, so have a greater angular distance from each other than the amount of the angle section. Adapter system according to at least one of the preceding claims, characterized in that the maximum radial distance of the transmission-side hole pattern is smaller than the maximum radial distance of the motor-side hole pattern, wherein the first wall portion ( 243 ) is arranged radially further inboard than the second wall section (FIG. 244 ), in particular wherein the second wall section ( 244 ) is formed from a plurality of subsections, in particular wherein the subsections are circumferentially spaced from each other, in particular wherein the subsections in the axial and in the radial direction overlap a region which also from the first wall portion ( 243 ) is respectively covered, in particular wherein the outer wall of the first wall portion ( 243 ) has at least one trapezoidal radial recess, in particular so that the vertical projection of the radial recess in a plane whose normal is directed in the axial direction is a trapezoid, in particular wherein the first wall section ( 243 ) at least one recess ( 241 ), wherein the recess ( 241 ) narrows with increasing radial distance in the circumferential direction. Gear motor, comprising - a gear housing, - a motor housing, - a driving shaft, which in the gear housing by means of a motor-side bearing ( 65 ), and - an adapter with a gear-side hole pattern, in particular wherein the adapter is arranged between the gear housing and the motor housing, characterized in that a quotient d / R is less than 0.6, in particular less than 0.4, where d is the inner diameter of the engine-side bearing ( 65 ), wherein R is the maximum radial distance of the gear-side hole pattern to the rotor shaft axis, wherein the adapter is in one piece, so one piece, executed, wherein the adapter between the transmission housing and the motor housing is interposable. Geared motor series whose variants can be produced and / or manufactured from a modular system, wherein the modular system comprises at least one adapter with a gear-side hole pattern, at least one motor ( 68 ) with a motor housing and a rotor shaft mounted therein ( 20 ), - at least a first and second transmission ( 74 . 740 ) each having a driving shaft, which in each case by means of a motor-side bearing ( 65 ) is mounted in a respective gear housing and - at least one coupling for connecting the rotor shaft ( 20 ) of the motor ( 68 ) and the driving shaft of the transmission ( 74 . 740 ), in particular wherein the adapter between engine ( 68 ) and gearboxes ( 74 . 740 ), wherein the gear housing has a hole pattern corresponding to the transmission side hole pattern of the adapter, so that a screw connection can be executed, wherein the first and second gear ( 74 . 740 ) differ in the inner diameter of the engine-side bearing ( 65 ) of the driving shaft of the transmission ( 74 . 740 ), characterized in that the gear-side hole pattern of one or the adapter for at least the two transmissions ( 74 . 740 ), in particular therefore first and second transmission ( 74 . 740 ), the same, wherein the coupling is a coupling sleeve ( 3 ), wherein the coupling sleeve ( 3 ) is surrounded by the adapter at least partially housing forming, in particular wherein the maximum outer diameter of the coupling sleeve ( 3 ) is greater than the minimum inner diameter of the adapter. Geared motor series according to at least one of the preceding claims, characterized in that the modular system has a plurality of adapters which have different motor-side hole patterns, so that different motors ( 68 . 680 . 681 . 682 . 683 ) are connectable, wherein the gear-side hole pattern of the adapter is the same, and / or that the two gear ( 74 . 740 ) differ in the respective quotient d / R, where d is the inner diameter of the respective motor-side bearing ( 65 ), where R is the maximum radial distance of the respective gear-side hole pattern to the rotor shaft axis, in particular wherein the quotient d / R is less than 0.6, in particular wherein the quotient d / R is less than 0.4, and / or that of partially overlapping the region axially covered by the adapter and the region axially covered by the coupling, the coupling being radially spaced from the adapter, in particular the coupling being the coupling sleeve ( 3 ) and a coupling hub part ( 1 ), wherein the coupling sleeve ( 3 rotatably, in particular form-fitting, in particular by means of a Curved toothing, with the coupling hub part ( 1 ), in particular wherein the coupling sleeve ( 3 ) rotatably, in particular form-fitting, with the rotor shaft ( 20 ) of the motor ( 681 ), in particular wherein the coupling hub part ( 1 ) rotatably with the driving shaft of the transmission ( 74 ), in particular wherein the coupling sleeve ( 3 ) the coupling hub part ( 1 ), in particular in an axially directed recess of the coupling sleeve ( 3 ), and / or wherein the coupling sleeve ( 3 ) the coupling hub part ( 1 ) axially at least partially covered and / or wherein the coupling sleeve ( 3 ) the coupling hub part ( 1 ) radially overlapped, in particular wherein the connection region between the coupling sleeve ( 3 ) and the coupling hub part ( 1 ) is axially spaced from the axially covered region of the adapter, in particular wherein the maximum outer radius of the coupling sleeve ( 3 ) to the engine ( 681 ), in particular wherein the radial extent of the free space 27 between the coupling sleeve ( 3 ) and the adapter to the engine ( 681 ) increases. Manufacturing method for a geared motor from a gearbox, in particular according to at least one of the preceding claims, wherein the gearbox as parts - at least one adapter with a gear-side hole pattern, - at least one motor ( 68 ) with a motor housing and a rotor shaft mounted therein ( 20 ), - at least a first and second transmission ( 74 . 740 ) each having a driving shaft, which in each case by means of a motor-side bearing ( 65 ) is mounted in a respective gear housing and - at least one coupling for connecting the rotor shaft ( 20 ) of the motor ( 68 ) and the driving shaft of the transmission ( 74 . 740 ), characterized in that optionally a first or second geared motor variant is produced from the parts of the gearbox assembly, wherein the first variant of the first gearbox ( 74 ) of the gearbox, the engine ( 68 ) of the gear box, the adapter of the gear box and the coupling of the gear box is formed, wherein the second variant of the second gear ( 740 ) of the gearbox, the engine ( 68 ) of the gear box, the adapter of the gear box and the coupling of the gear box is formed, wherein the adapter used in the first variant and the adapter used in the second variant are the same, in particular identical, wherein the inner diameter of the engine-side bearing ( 65 ) of the first transmission ( 74 ) is different from the inner diameter of the engine-side bearing ( 65 ) of the second transmission ( 740 ), in particular wherein the gear-side hole pattern used for the connection of one or the adapter for at least the two transmissions ( 74 . 740 ), in particular therefore first and second transmission ( 74 . 740 ), is equal to.

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