Geared motor with reducer, motor and adapter flange

Abstract

The present invention relates to a geared motor comprising a reducer, a motor and an adapter flange, in particular, the adapter flange arranged between the reducer and the motor, wherein the adapter flange comprises an annular base body which is shaped rotationally symmetrically with respect to the rotation axis of an input shaft of the reducer, an axial protrusion being formed on the base body, wherein the axial protrusion is arranged on a side of the adapter flange facing away from the motor, wherein the axial protrusion is designed to be interrupted in the circumferential direction, and a housing component extends into the interrupted region.

Description

Technical Field

[0001] The invention relates to a reduction motor comprising a reducer, a motor and an adapter flange. Background Art

[0002] It is generally known that a speed reducer includes a shaft rotatably supported by a bearing and a toothed member. Summary of the Invention

[0003] The object of the present invention is therefore to improve a geared motor, wherein the geared motor should be cost-effective to produce and should be compact.

[0004] In terms of the geared motor, the important feature of the present invention is that the geared motor comprises a reducer, a motor and an adapter flange, in particular an adapter flange arranged between the reducer and the motor.

[0005] The adapter flange has an annular base body which is shaped rotationally symmetrically with respect to the rotation axis of the input shaft of the reducer and on which an axial projection is formed.

[0006] The axial projection is arranged on the side of the adapter flange facing away from the motor.

[0007] wherein the radial distance region (or radial length range) covered by the housing part overlaps the radial distance region covered by the axial projection in the circumferential angle region not covered by the axial projection,

[0008] wherein the area covered by the housing component in the axial direction overlaps the area covered by the axial projection in the axial direction, in particular in the circumferential angle area not covered by the axial projection and in the radial distance area covered by the axial projection,

[0009] Overlapping with the radial distance region covered by the axial projection,

[0010] In particular, the axial direction is parallel to the rotation axis of the input shaft, the radial distance is the distance with respect to the rotation axis of the input shaft, and / or the circumferential direction relates to this rotation axis of the input shaft,

[0011] - or wherein the axial projection is designed to be interrupted in the circumferential direction, the housing component protruding into the region of the interruption.

[0012] The advantage is that the axial projection, while being designed to be suitable for centering the motor and the reducer, is also designed to be as compact as possible. This is because centering requires at least a cylindrical, finely machined surface on which the alignment is performed. However, according to the present invention, the cylindrical surface is interrupted in the circumferential direction, i.e., it is not designed to be completely circumferential. This interrupted area can then be utilized as a subregion of the housing component, which, in order to form a housing, surrounds the largest toothed component of the reducer, namely the gear that is connected to the output shaft in a rotationally fixed manner.

[0013] Preferably, the circumferential angular area of the interruption is smaller than 180°.

[0014] Another advantage of the present invention is that the type of flange connection for the adapter flange facing the motor—that is, a round flange—is different from the type of flange connection for the reducer, such as a square flange. Consequently, the hole patterns can be used differently. For example, a rectangular hole pattern can be used facing the reducer, while a polygonal, more circular, hole pattern can be used facing the motor.

[0015] In this case, the radial distance area covered by the holes of the hole pattern facing the motor can even overlap the radial distance area covered by the holes of the hole pattern facing the reducer. However, all holes of the two hole patterns are spaced apart from each other in the circumferential direction. The holes of both hole patterns are preferably designed to pass through the adapter flange.

[0016] In particular, the first hole pattern, intended for use with the reducer, is arranged only within the circumferential angular region covered by the axial projection. The second hole pattern, intended for use with the motor, also overlaps the circumferential angular region covered by the interrupted region of the axial projection. Consequently, the axes of symmetry of the discrete rotational symmetry of the two hole patterns are not coincident but rather spaced apart from one another. This allows for a particularly compact design of the adapter flange. This is because the spacing of the axes of symmetry creates the interrupted region between the annular base of the adapter flange and the housing component of the reducer.

[0017] In an advantageous embodiment, the adapter flange is connected to a circular flange toward the motor and to a rectangular or square flange toward the reducer. This has the advantage that different flange types with correspondingly different hole patterns and centering surfaces can be provided.

[0018] In an advantageous embodiment, the adapter flange has, on its side facing the motor, a first axially oriented eyelet, through which a connecting element, such as a screw or a bolt, projects, which also projects through the supporting flange of the motor.

[0019] The hole pattern of the first bore has discrete rotational symmetry, in particular greater than sixfold rotational symmetry, relative to the rotational axis of the input shaft. This has the advantage that the rotational axis of the rotor shaft of the electric machine is centered, in particular centrally, relative to the adapter flange. This allows for stable fixing of the adapter flange.

[0020] In an advantageous embodiment, the adapter flange has, on its side facing the reducer, an axially oriented second eyelet which extends through the axial projection of the adapter flange and the annular ring body of the adapter flange.

[0021] In this case, a connecting element, such as a screw or a bolt, projects through the second eyelet and is screwed into a threaded hole formed in the housing component.

[0022] In particular, the hole pattern of the second bore has discrete rotational symmetry, in particular two-fold rotational symmetry, based on an axis of symmetry spaced apart from the rotational axis of the input shaft and parallel to the rotational axis. This has the advantage that the geared motor can be designed more compactly, since the mechanical interfaces on the gear unit side, in particular the centering and securing devices, are displaced and arranged in such a way that an interrupted region of the axial projection can be provided and at least partially filled by accommodating a toothed element connected to the output shaft.

[0023] In an advantageous embodiment, the adapter flange is centered on the receiving part of the reducer, in particular, the adapter flange is aligned and centered coaxially with the rotational axis of the input shaft on the receiving part of the reducer.

[0024] In this case, the receiving part is aligned, in particular centered, on the housing part of the gear unit, in particular by means of a cylindrical centering collar.

[0025] In particular, the receiving part is connected to the housing part by means of screws,

[0026] In particular, the receiving component is held pressed against the housing component by the screw heads of screws screwed into axially oriented threaded holes in the housing component. This has the advantage that the adapter flange is centered on the receiving component, in which the bearing of the input shaft is accommodated. Therefore, the receiving component that accommodates the bearing arrangement, rather than the housing component of the reducer, is used for centering. The motor is thus centered on the adapter flange with its supporting flange facing the adapter flange, which in turn is centered on the receiving component, in which the bearing of the input shaft is centrally accommodated. In this way, the motor—particularly its rotor shaft, which is supported by the bearings accommodated in the supporting flange—is aligned coaxially with the input shaft of the reducer.

[0027] In an advantageous embodiment, a bearing is accommodated in the receiving element, the inner ring of each bearing being placed onto the input shaft.

[0028] In one advantageous embodiment, the annular ring body is designed to be completely circumferential in the circumferential direction, in particular, to be formed without interruptions. This has the advantage of achieving high stability. Furthermore, the rotationally symmetrical hole pattern can be arranged completely toward the motor, so that the motor can still be fixed in the interrupted areas. The reducer can also be fixed without interruptions, because the hole pattern can be arranged in the axial projection and thus establish a stable connection between the adapter flange and the housing part of the reducer.

[0029] In an advantageous embodiment, the maximum value of the radial distance region covered by the axial projection has four local maxima as a function of the circumferential angle.

[0030] In particular, each circumferential angle region covered by the second eyelet contains a circumferential angle corresponding to a corresponding local maximum. Advantageously, the eyelets of the hole pattern facing the reducer are arranged in a radially wider region of the axial projection.

[0031] In an advantageous embodiment, the axial projection has a finish-machined surface facing the reducer, the minimum radial distance of which is constant in a sub-region of the circumferential angular region covered by the axial projection.

[0032] In particular, the subregion covers more than 80% of the circumferential angular region covered by the axial projection. This has the advantage that precise centering can be achieved.

[0033] In an advantageous embodiment, the cover part is connected to the receiving part, in particular sealingly by means of an intermediately arranged seal, in particular a flat seal.

[0034] A shaft sealing ring is accommodated in the cover component and seals against the input shaft. In particular, the sealing lip of the shaft sealing ring operates on a sealing surface provided on the input shaft. This has the advantage that the input region, in particular the bearing structure of the input shaft, is sealed oil-tight. Furthermore, the shaft sealing ring is activated by attaching and connecting the cover component, further improving the sealing. The cover component has a centering flange, which can be used to align the cover component on the receiving component. This ensures that the shaft sealing ring accommodated in the cover component is coaxially centered with the input shaft of the reducer, even though the bearing is accommodated in the receiving component. Consequently, the bearing seat can be machined in a single step during manufacturing using a machine tool.

[0035] In an advantageous embodiment, the pressure ring and the clamping ring are placed on the input shaft, wherein the pressure ring rests on a first bearing of the bearings.

[0036] The clamping ring is connected to the input shaft in a force-locking / friction-locking manner.

[0037] In particular, an axially oriented bolt is supported on the clamping ring and screwed into an axially oriented threaded hole in the pressure ring, so that the bolt supported on the clamping ring presses the pressure ring onto the first bearing, in particular onto the inner ring of the first bearing. This has the advantage that a simple arrangement can be used to generate the bearing pressure force.

[0038] In an advantageous embodiment, the housing of the shaft end pump is connected to the housing part, and the intermediate shaft of the reduction gear is connected to the rotatable part of the shaft end pump in a rotationally fixed manner, in particular driving the rotatable part. This has the advantage that the oil can be conveyed passively, i.e., in particular not by means of an electrically driven pump, but by means of a pump driven by the intermediate shaft that rotates during operation.

[0039] In an advantageous embodiment, the oil delivered from the oil sump by the shaft end pump passes through a first channel arranged in the housing component, in particular through a first channel arranged in the housing component and extending through the housing component, and through a second channel to a bearing arranged further away from the intermediate shaft, the first channel opening into the second channel extending through the receiving component.

[0040] In particular, the first channel is formed by a bore formed in the housing part and / or the second channel is formed by a bore formed in the receiving part. This has the advantage that passive lubrication of the bevel gear stage and in particular its bearings is possible even if the input shaft is oriented vertically, that is, the axis of rotation of the input shaft is oriented parallel to the direction of gravity.

[0041] In one advantageous embodiment, a fourth channel is arranged in the receiving component and is designed mirror-symmetrically to the second channel, particularly about a mirror plane containing the axis of rotation of the input shaft. This has the advantage that the shaft end pump can alternatively be arranged at the other end of the intermediate shaft, thereby providing the same channel structure. Alternatively, a shaft end pump can be provided at each end of the intermediate shaft. Thus, an intermediate shaft that rotates slower than the input shaft can still be used to deliver a high oil flow. This is because two shaft end pumps, even if driven relatively slowly, can still deliver a high oil flow.

[0042] In an advantageous embodiment, the first channel comprises a first, radially oriented blind hole formed in the housing component, which opens into a second, axially oriented blind hole formed in the housing component and sealed with a closing plug from the surroundings, the second blind hole intersecting a third, radially oriented hole extending through the housing component, the third hole opening into a fourth, radially oriented hole formed in the receiving component, the fourth hole intersecting a fifth, axially oriented blind hole formed in the receiving component.

[0043] In particular, the fourth bore is only partially closed toward the input shaft by means of a plug and / or is arranged in an oil-permeable manner, wherein the plug is arranged in the axial direction between the bearings of the input shaft, so that the oil delivered by the shaft end pump flows from the fourth bore, past the plug, in the axial direction between the bearings of the input shaft, and supplies the bearing of the two bearings of the input shaft that is arranged below the fourth bore with oil.

[0044] In particular, the first channel has an outlet located above the bearing of the input shaft. This has the advantage that the upper bearing of the bearings is supplied with oil via the outlet and the lower bearing of the bearings is supplied with oil via the plug arranged in an oil-permeable manner.

[0045] In an advantageous embodiment, the first channel comprises a first hole, a second hole, a third hole, a fourth hole, and a fifth hole. This has the advantage that forming the holes allows for simple manufacturing. However, it is particularly advantageous to use blind holes, since these do not require closing plugs.

[0046] In one advantageous embodiment, the receiving part has four radial bores extending through the receiving part and spaced apart from one another in the circumferential direction. The four radial bores are arranged at the same axial position, i.e., in particular, cover the same axial area. This has the advantage that, on the one hand, at least one of the bores serves as an inlet for the oil, and thus the oil is filtered and conveyed into the gap area between the input shaft and the receiving part, so that the oil flows downwardly along the bearing of the two input shaft bearings, whichever is arranged further down in the direction of gravity, on the input shaft.

[0047] In an advantageous embodiment, the input shaft is connected to a bevel pinion in a rotationally fixed manner, and the bevel pinion meshes with a bevel gear that is connected to the intermediate shaft in a rotationally fixed manner.

[0048] The intermediate shaft is connected to the helical gear in a manner that is non-rotatable relative to the intermediate shaft, and the helical gear is meshed with a gear that is connected to the output shaft of the reducer in a manner that is non-rotatable relative to the intermediate shaft.

[0049] In particular, a washer, held in a form-fitting manner by a screw screwed into the input shaft, delimits the bevel pinion in the axial direction. This has the advantage that the bevel gear stage at the input is followed by a spur gear stage. The gears of the spur gear stage can be designed with helical toothing, thus achieving low-noise operation.

[0050] For a person skilled in the art, further sensible combinations of features of the description and / or of the drawings will appear, in particular from the posed technical problem and / or from a comparison with the prior art. BRIEF DESCRIPTION OF THE DRAWINGS

[0051] Now the present invention is described in detail according to the schematic diagram:

[0052] exist Figure 1 1 shows an oblique view of a reduction gear having an adapter flange 3 for connection to an electric motor 120 .

[0053] exist Figure 2 The reducer is shown from another viewing direction.

[0054] exist Figure 3 The reducer is shown in section.

[0055] exist Figure 4 Another cross-sectional view of the reducer is shown in FIG.

[0056] exist Figure 5 : shows a cross section of the reducer perpendicular thereto.

[0057] exist Figure 6 The reducer with the adapter flange 3 is shown in FIG. Figure 1 Corresponding top view.

[0058] exist Figure 7 , the reducer is shown in an oblique view with an adapter flange 3 shown in exploded form.

[0059] exist Figure 8 , the adapter flange 3 is shown in an oblique view from a first viewing direction.

[0060] exist Figure 9 , the adapter flange 3 is shown in an oblique view from a second viewing direction.

[0061] exist Figure 10 The cross section of the gear unit is shown in FIG. 1 such that the input region of the gear unit is visible.

[0062] exist Figure 11 The shaft, toothed components and bearings of the reducer are shown in an oblique view, wherein the housing component 1 of the reducer and the lubricating oil of the reducer are omitted.

[0063] exist Figure 12 The reducer connected to the motor 120 is shown in an oblique view. DETAILED DESCRIPTION

[0064] As shown in the drawings, an adapter flange 3 is arranged between the motor 120 and the housing component 1 of the reducer, so that the motor 120 can be centered on the adapter flange and mounted on the adapter flange 3 by means of bolts.

[0065] The adapter flange 3 is centered on the housing part 1 and is connected to the housing part 1 by means of screws.

[0066] The adapter flange 3 has a circular outer shape on the side thereof facing the motor 120. In particular, the largest outer circumference of the adapter flange 3 is designed to be circular, in particular, to be designed as a cylindrical outer contour.

[0067] The mechanical interface to the electric motor 120, in particular the mechanical interface with the centering ring and the hole pattern, has rotational symmetry, in particular about the rotation axis of the input shaft 4. The rotational symmetry is at least discrete, but can also be designed to be continuous.

[0068] The radial distances here are always based on the rotation axis of the input shaft 4. Likewise, the axial direction is parallel to the rotation axis of the input shaft 4. The circumferential direction is also based on the rotation axis of the input shaft 4.

[0069] The adapter flange 3 has, on its side facing the reducer housing, an axial projection 90 which projects axially toward the housing component 1, but which is interrupted in the circumferential direction by a thinned wall region 92. The thinned wall region 92 has a smaller extent in the axial direction, in particular a smaller wall thickness, than in the circumferential angular region covered by the axial projection 90.

[0070] That is, the adapter flange 3 preferably has an annular base body that is designed to be rotationally symmetrical about the rotation axis of the input shaft 4 of the reducer, and an axial projection 90 is formed on the base body on the reducer side. However, the axial projection is not rotationally symmetrical but is interrupted in a circumferential angular region. The housing component 1, in particular, a convex portion of the housing component 1 that at least partially surrounds the output gear 113 in a housing-forming manner, extends into this interrupted circumferential angular region, wherein the radial distance region covered by the housing component 1 in this interrupted region—that is, in this circumferential angular region and in the region covered by the base body in the axial direction—overlaps with the radial distance region covered by the base body.

[0071] The housing component 1 therefore projects into the region of the interruption of the axial projection 90 .

[0072] Axially oriented holes 91 are formed in the axial projection 90 , in particular forming a rectangular, in particular square, hole pattern.

[0073] The screws for connecting the housing part 1 to the adapter flange 3 are therefore arranged in a rectangular arrangement.

[0074] That is, a square flange may be used toward the speed reducer, while a round flange may be used toward the motor 120 .

[0075] The axial projection 90 covers only a portion of the entire circumferential angle range. The radial distance of maximum coverage has four local maxima in relation to the circumferential angle.

[0076] The circumferential angle region covered by the corresponding hole 91 contains the circumferential angle value of the respective maximum.

[0077] The corresponding eyelets 91 are therefore each arranged in the radially widened region of the axial projection 90 .

[0078] The axial projection 90 has an inner cylindrical surface area on its inner circumference, ie at its smallest radial distance, which surface area is however interrupted in the angular area of the circumference not covered by the axial projection 90 .

[0079] This inner circumference serves as a receptacle for centering the receptacle element 41 of the reducer. The inner cylindrical surface area is aligned coaxially with the axis of rotation of the input shaft 4 .

[0080] Furthermore, the axial projection has a finely machined, axially projecting annular surface in the circumferential angle region covered by the axial projection 90 .

[0081] By means of this annular surface, the adapter flange 3 is placed on the finely machined, flat surface area of the housing component 1. In this case, corresponding axially oriented holes, in particular threaded holes, are formed in each of the finely machined, flat surface areas, wherein screws are passed through the eyelets 91 and screwed into the threaded holes 71 formed in the finely machined, flat surface area of the housing component 1.

[0082] The annular surface of the axial projection 90 and the surface area in which the eyelet 91 is formed are located at the same axial position, which is the position farthest from the motor 120 and covered by the adapter flange 3 .

[0083] The thinned wall region 92 of the adapter flange 3 lies flat on, or at least has only a small distance from, a curvature, in particular a raised portion, of the housing part 1. The curvature at least partially surrounds, forming a housing, a gear wheel 113 connected to the output shaft.

[0084] The output shaft 5 is oriented perpendicularly to the input shaft 4 .

[0085] Gear 113 , which is rotationally fixedly connected to output shaft 5 , together with the camber covers an area in the axial direction, ie, perpendicularly to the rotation axis of the input shaft, which includes the area covered by bearing 47 of input shaft 4 .

[0086] Electric motor 120 has a stator housing that is axially connected on both sides to a supporting flange, each designed as a circular flange. Each of the two supporting flanges accommodates a bearing that is mounted on the rotor shaft of electric motor 120. The rotor shaft is thus rotatably supported by the two bearings accommodated in the supporting flanges.

[0087] The two support flanges are designed as circular flanges. Therefore, they have a substantially circular outer circumference. The hole pattern for the connecting screws for connecting the first of the two support flanges to the adapter flange 3 has a discrete rotational symmetry, wherein the axis of rotational symmetry corresponds to the rotational axis of the rotor shaft, specifically, the rotational axis of the input shaft 4 arranged coaxially therewith. The hole pattern of the adapter flange 3, which faces the first support flange of the electric machine 120, also has this discrete rotational symmetry.

[0088] The bearing 47 is received in a receiving part 41 which has a radially outwardly projecting, circumferentially circumferentially extending collar which is pressed against the housing part 1 by means of screws screwed into axially oriented threaded holes in the housing part 1 .

[0089] In this case, a step is finished on the flange and is therefore designed to be suitable for centering on the housing part 1 .

[0090] A bearing 47 is mounted on the input shaft 4 , thereby rotatably supporting the input shaft.

[0091] The cover part 46 is pressed onto the receiving part 41 by means of screws screwed into threaded holes of the receiving part 41, in particular by means of the screw heads of these screws. A shaft sealing ring 45 is accommodated in the cover part 46, which seals the cover part 46 toward the input shaft 4.

[0092] A clamping ring 50 and a pressure ring 52 are mounted on the input shaft 4 and rest against the first bearing of the bearings 47. The clamping ring 50 is connected to the input shaft 4 in a force-locking manner. An axially oriented bolt 51 is supported on the clamping ring 50 and screwed into an axially oriented threaded hole in the pressure ring 52. The bolt supported on the clamping ring 50 presses the pressure ring 52 against the first bearing. In particular, the pressure ring 52 presses against the inner ring of the first bearing.

[0093] The input shaft 4 passes through the cover member 46. The input shaft 4 is connected to a bevel pinion 49 in a rotationally fixed manner, the teeth of which mesh with the teeth of the gear 48, in particular the bevel gear.

[0094] The outer ring of the first bearing rests on a shoulder of the receiving part 41 .

[0095] The bevel pinion 49 is placed onto the conical end region of the input shaft 4 and is axially fixed by means of a washer which is pressed against the end face of the input shaft 4 by a screw screwed centrally into the end face of the input shaft 4. Furthermore, the bevel pinion 49 is connected in a non-positive and / or positive manner, in particular by means of a key connection.

[0096] An axially protruding centering collar extending around the circumference is integrally formed on the cover part 46 , said centering collar being aligned and centered on a centering seat formed on the receiving part 41 .

[0097] The bevel-toothed pinion 49 meshes with the toothing of the gear 48 , in particular the toothing of a bevel gear.

[0098] The gear 48 is connected to an intermediate shaft 111 in a rotationally fixed manner, which is rotatably supported by a bearing received in a housing part and is connected to a toothed section 112 in a rotationally fixed manner, which meshes with the toothed section of a gear 113, which is connected to the output shaft 5 in a rotationally fixed manner.

[0099] Therefore, the preferably two-stage reduction gear according to the invention has an input bevel gear stage followed by an output-side spur gear stage. The teeth of the spur gear stages preferably each have a non-zero inclination angle.

[0100] The intermediate shaft 111 is connected to the shaft end pump 100. Therefore, although the shaft end pump is not driven by the fast-rotating input shaft 4 but is driven by the intermediate shaft 111, the intermediate shaft 111 at least rotates faster than the output shaft 5.

[0101] The oil level of the oil in the inner space of the reducer covers or reaches the pinion gear teeth. However, the two bearings 47 of the input shaft 4 are arranged above the oil level and are therefore not lubricated after the reducer has been stopped for a long time.

[0102] Therefore, once the reducer is running, the shaft end pump 100 driven by the intermediate shaft 111 pumps oil from the oil pool arranged below the oil level to a position above the bearing 47, so that the bearing 47 is lubricated and the shaft seal ring 40 does not run dry.

[0103] The input shaft 4 is parallel to the normal direction of the oil pool surface, especially when the reducer is stopped for a long time.

[0104] The other bearings, the toothing and the gearwheels (48, 113) are always at least partially immersed in the oil sump of the reducer.

[0105] like Figure 10 As shown, the shaft end pump 100 delivers oil into a radially oriented bore 101 of the housing part 1. This bore is machined from the outside as a blind hole and opens into an axially oriented bore 102 of the housing part 1, which is also machined from the outside, designed as a blind hole, and is closed at its end facing the motor 120 with a closing plug 105.

[0106] A radially oriented hole 103 passing through the housing part 1 intersects the hole 102 and opens into a radial hole 108 formed in the receiving part 41 and passing through the receiving part 41. This radial hole is closed toward the input shaft 4 by means of a plug 107, but this plug is not completely sealed, but rather allows a small amount of oil to pass through, which then reaches the lower bearing 47, that is, which is further away from the electric motor 120, in the gap between the housing part 1 and the input shaft 4.

[0107] An axially oriented blind hole 106 formed from the outside in the receiving part 41 opens into the radial bore 108, so that the oil delivered by the shaft end pump 100 flows out at the end of the receiving part 41 facing the cover part 46 and supplies the upper bearing 47, that is, facing the motor 120, with oil. The second bearing arranged below the first bearing is then also supplied with oil.

[0108] The two bearings 47 are preferably designed as radial thrust bearings.

[0109] The receiving part 41 , which is connected to the housing part 1 in an oil-tight manner, together with the cover part 46 , which is connected to the receiving part 41 in an oil-tight manner, encloses an interior area of the reducer.

[0110] When the reducer is running and therefore when the intermediate shaft 111 rotates, the oil is delivered by the shaft end pump 100 in the opposite direction of gravity and thus lubricates the bearing 47 with oil. In addition, the oil flowing past the bearing 47 absorbs heat loss, which is then discharged from the oil pool to the surrounding environment.

[0111] In order to achieve the lowest possible heat transfer resistance from the oil sump to the surroundings, a region with recesses 30 , which are particularly regularly spaced apart from one another, is formed on the inside of the housing part 1 .

[0112] In these regions, the wall thickness is preferably not constant, but rather these regions are designed to be smooth, in particular flat, on their outer sides.

[0113] The wall thickness therefore changes in these regions synchronously with the recesses 30 .

[0114] Here, each of the recesses 30 extends longer in a direction perpendicular to the axial direction, ie, perpendicular to the rotation axis of the input shaft 4 , than in the axial direction.

[0115] Preferably, the recesses 30 are arranged below the oil level and thus provide an increased surface area on the inside, so that the heat transfer resistance from the oil to the housing component 1 is reduced, and heat can be absorbed in the areas arranged between the recesses 30, in particular thickened by the flat structure of the corresponding areas on the outside, in particular due to the greater heat capacity generated by the thickening. From there, the heat is then diffused in the housing component 1 and dissipated to the surrounding environment.

[0116] In other areas, recesses 2 are provided on the outside of the housing part, wherein the wall thickness is constant in these other areas. Accordingly, corresponding recesses are formed not only on the outside, in particular on the outside with recesses 2 regularly spaced apart from one another, but also on the inside.

[0117] Here, each of the recesses 2 also extends longer in a direction perpendicular to the axial direction, ie, perpendicular to the rotational axis of the input shaft 4 , than in the axial direction.

[0118] Thus, the recess 2 can be formed on the housing part 1 in order to achieve a special design impression that indicates the source. In contrast, the recess 30 formed only on the inner side is not used for a design impression, but for improving heat dissipation.

[0119] On the underside of the reducer, the interior is enclosed by a reducer cover 31. This cover also features the recess 2 and a constant wall thickness, but features intersecting reinforcement ribs 32 molded onto its inner side. This provides a rigid design and a distinctive appearance, while also stabilizing the underside of the oil sump. The flowing oil must overcome not only the reinforcement ribs 32 but also the recesses and ridges between them. Consequently, the oil in the oil sump experiences less laminar flow and more turbulent flow as it moves. This also improves heat transfer from the oil to the reducer cover 31.

[0120] A radial bore 43 is arranged in the receiving part 41 and extends through the receiving part 41 at a distance from the radial bore 108 in the circumferential direction. An axially oriented blind hole formed in the receiving part opens into the radial bore, the blind hole projecting from the receiving part 41 toward the oil sump. This allows oil to be drained from the spatial region between the input shaft and the receiving part. In particular, in the event of an overpressure in this region, this oil can be drained for pressure relief.

[0121] The radial bore 43 is closed radially outwardly by means of the housing part 1, into which the receiving part 41 projects. Mirror-symmetrically with respect to a plane of symmetry containing the axis of rotation of the input shaft, the receiving part 41 has another such pressure relief.

[0122] This means that the receiving part 41 has in this way four radial holes at the same axial position, which are spaced apart from one another in the circumferential direction and which pass through the receiving part.

[0123] In other exemplary embodiments according to the invention, the bevel pinion 49 is designed integrally, in particular integrally, with the input shaft.

[0124] List of reference numerals:

[0125] 1 Housing components

[0126] 2 concavity

[0127] 3 Adapter flange

[0128] 4 Input shaft

[0129] 5 Output shaft

[0130] 30 concavity

[0131] 31 Reducer cover

[0132] 32 reinforcement ribs

[0133] 40 Shaft seal ring

[0134] 41 Receiving parts

[0135] 42 bolts

[0136] 43 radial holes

[0137] 44 axial hole

[0138] 45 shaft seal ring

[0139] 46 Cover parts

[0140] 47 Bearings, especially tapered roller bearings

[0141] 48 Gears, especially bevel gears

[0142] 49 bevel pinion

[0143] 50 Clamping ring

[0144] 51 bolts

[0145] 52 clamping ring

[0146] 60 bolts

[0147] 61 First hole

[0148] 71 holes, especially threaded holes

[0149] 90 Axial protrusion

[0150] 91 Second eyelet

[0151] 92 Thinned wall area

[0152] 100 Shaft end pump

[0153] 101 radial holes

[0154] 102 axial hole

[0155] 103 radial holes

[0156] 104 Closure plug

[0157] 105 Closure plug

[0158] 106 axial hole

[0159] 107 plug

[0160] 108 radial holes

[0161] 111 intermediate shaft

[0162] 112 teeth

[0163] 113 Gear

[0164] 120 motor

Claims

1. A reduction motor comprising a reducer, a motor and an adapter flange. in, The adapter flange is arranged between the reducer and the motor so that the motor can be centered on the adapter flange and can be mounted on the adapter flange. The adapter flange has an annular base body which is shaped rotationally symmetrically with respect to the rotation axis of the input shaft of the reducer and on which an axial projection is formed. The axial projection is arranged on the side of the adapter flange facing away from the motor. wherein the radial distance region covered by the housing part overlaps the radial distance region covered by the base body of the adapter flange in the circumferential angle region not covered by the axial projection, wherein the area covered by the housing component in the axial direction overlaps the area covered by the axial projection in the axial direction in a circumferential angle area not covered by the axial projection and in a radial distance area covered by the axial projection, wherein the axial direction is parallel to the rotation axis of the input shaft, the radial distance is the distance about the rotation axis of the input shaft, and / or the circumferential direction relates to this rotation axis of the input shaft, - or wherein the axial projection is designed to be interrupted in the circumferential direction, the housing component protruding into the region of the interruption.

2. The reduction motor according to claim 1, It is characterized in that The adapter flange is connected to the round flange facing the motor and to the rectangular or square flange facing the reducer.

3. The reduction motor according to claim 1 or 2, It is characterized in that The adapter flange has, on its side facing the motor, a first axially oriented eyelet (61), through which the connecting element projects, and which also projects through the supporting flange of the motor. The hole pattern of the first bore has a discrete rotational symmetry relative to the rotation axis of the input shaft, wherein the rotational symmetry is greater than sixfold.

4. The reduction motor according to claim 3, It is characterized in that The adapter flange has an axially oriented second hole (91) on its side facing the reducer, which second hole passes through the axial protrusion of the adapter flange and the annular ring body of the adapter flange. wherein the connecting element projects through the second eyelet (91) and is screwed into a threaded hole formed in the housing component, The hole pattern of the second bore has a discrete rotational symmetry based on parallel symmetry axes spaced apart from the rotational axis of the input shaft, wherein the discrete rotational symmetry is a two-fold rotational symmetry.

5. The reduction motor according to claim 1 or 2, It is characterized in that The adapter flange is centered on the receiving part of the reducer, the adapter flange being aligned and centered coaxially with the axis of rotation of the input shaft. In this case, the receiving part is aligned on the housing part of the gear unit by means of a cylindrical centering collar. The receiving part is connected to the housing part by means of screws. In this case, the receiving part is held pressed against the housing part by the screw head of a screw screwed into an axially oriented threaded hole in the housing part.

6. The reduction motor according to claim 5, It is characterized in that The receiving component receives a bearing, the inner ring of each bearing being mounted on the input shaft. and / or The annular ring body is designed to be completely circumferential in the circumferential direction and is shaped without interruptions.

7. The reduction motor according to claim 4, It is characterized in that The maximum value of the radial distance region covered by the axial projection has four local maxima in relation to the circumferential angle, Each circumferential angle region covered by the second eyelet (91) contains a circumferential angle corresponding to a corresponding local maximum.

8. The reduction motor according to claim 1 or 2, It is characterized in that The axial projection has a finish-machined face facing the reducer, the minimum radial distance of which is constant in a sub-region of the circumferential angular region covered by the axial projection, In this case, the subregion covers more than 80% of the circumferential angular region covered by the axial projection.

9. The reduction motor according to claim 5, It is characterized in that The cover part and the receiving part are connected in a sealing manner by means of a seal arranged in between. A shaft sealing ring is accommodated in the cover component, which seals toward the input shaft. A sealing lip of the shaft sealing ring operates on a sealing surface formed on the input shaft.

10. The reduction motor according to claim 6, It is characterized in that The pressure ring (52) and the clamping ring (50) are mounted on the input shaft, wherein the pressure ring (52) abuts against the first bearing (47) in the bearings. The clamping ring (50) is connected to the input shaft (4) in a force-locking manner. An axially oriented bolt (51) is supported on a clamping ring (50) and screwed into an axially oriented threaded hole of a pressure ring (52), so that the bolt supported on the clamping ring (50) presses the pressure ring (52) onto the inner ring of the first bearing (47).

11. The reduction motor according to claim 1 or 2, It is characterized in that The housing of the shaft end pump is connected to the housing component, and the intermediate shaft of the speed reducer is connected to the rotatable component of the shaft end pump in a relatively non-rotatable manner and drives the rotatable component.

12. The reduction motor according to claim 11, It is characterized in that The oil delivered from the oil sump by the shaft end pump passes through a first channel arranged in the housing component and through a second channel to a bearing arranged further away from the intermediate shaft. The first channel opens into a second channel extending through the receiving component. Therein, the first channel is formed by a hole formed in the housing component, and / or the second channel is formed by a hole formed in the receiving component.

13. The reduction motor according to claim 12, It is characterized in that A third channel is arranged in the housing component, the third channel being designed to be mirror-symmetrical to the first channel about a rotation axis containing the input shaft. and / or A fourth channel is arranged in the receiving component and is designed to be mirror-symmetrical to the second channel about a plane containing the rotation axis of the input shaft.

14. The reduction motor according to claim 13, It is characterized in that The first channel has a first, radially oriented blind hole formed in the housing component, which opens into a second, axially oriented blind hole formed in the housing component and sealed with a closing plug from the surroundings, the second blind hole intersecting a third, radially oriented hole extending through the housing component, the third hole opening into a fourth, radially oriented hole formed in the receiving component, the fourth hole intersecting a fifth, axially oriented blind hole formed in the receiving component, The fourth hole is only partially closed toward the input shaft by means of a plug and / or is arranged in an oil-permeable manner, wherein the plug is arranged in the axial direction between the bearings of the input shaft, so that the oil delivered by the shaft end pump flows from the fourth hole, past the plug, in the axial direction between the bearings of the input shaft, and supplies the bearing of the two bearings of the input shaft that is arranged below the fourth hole with oil. wherein the first channel has an outlet located above a bearing of the input shaft, The first channel includes a first hole, a second hole, a third hole, a fourth hole and a fifth hole. The receiving component has four radial holes which are spaced apart from each other in the circumferential direction and penetrate the receiving component. The four radial holes are arranged at the same axial position.

15. The reduction motor according to claim 1 or 2, It is characterized in that The input shaft is connected to the bevel pinion in a manner fixedly rotating relative to each other, and the bevel pinion is meshed with a bevel gear connected to the intermediate shaft in a manner fixedly rotating relative to each other. The intermediate shaft is connected to the helical gear in a manner that is non-rotatable relative to the intermediate shaft, and the helical gear is meshed with a gear that is connected to the output shaft of the reducer in a manner that is non-rotatable relative to the intermediate shaft. In this case, a washer, which is held in a form-fitting manner by a bolt screwed into the input shaft, delimits the bevel pinion in the axial direction.

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