Speed reducer motor with speed reducer, motor and adapter flange

Abstract

The invention relates to a reduction gear having a reduction gear, an electric machine and an adapter flange, in particular an adapter flange arranged between the reduction gear and the electric machine, wherein the adapter flange has a ring-shaped base body which is rotationally symmetrical about the rotational axis of the input shaft of the reduction gear, on which base body an axial protrusion is formed, wherein the axial protrusion is arranged on the side of the adapter flange facing away from the electric machine, wherein the axial protrusion is designed to be interrupted in the circumferential direction, a housing part penetrating into the interrupted region.

Description

TECHNICAL FIELD

[0001] The invention relates to a reduction gear motor having a reduction gear, an electric motor and an adapter flange. BACKGROUND

[0002] It is generally known that a reduction gear has a shaft which is rotatably supported by a bearing and a toothed component. SUMMARY

[0003] It is therefore an object of the invention to improve a reduction gear motor, wherein the production of the reduction gear motor should be cost-advantageous and the reduction gear motor should be compact.

[0004] According to the invention, the object is achieved in the case of a reduction gear motor in accordance with the features specified in claim 1.

[0005] An important feature of the invention in the case of the reduction gear is that the reduction gear has a housing which has a housing component which at least partially surrounds the toothed component and the oil in a housing-forming manner,

[0006] wherein

[0007] the wall thickness of the housing component fluctuates periodically, in particular in a straight-line direction, in one or more regions of the housing component,

[0008] in the one or more regions, the outer surface is designed to be smooth, in particular flat,

[0009] or a region having recesses, in particular recesses which are regularly spaced apart from one another, is provided on the inner side of the housing component, in particular on the surface facing the oil and / or the inner surface, in particular wherein the wall thickness varies in the one or more regions in synchronism with the recesses.

[0010] The advantage is that the inner surface is enlarged by the recesses and the thermal resistance from the oil to the housing is thus reduced. Furthermore, by virtue of the smooth, in particular flat, outer surface, the thermal capacity for the heat flow into the housing is increased, although the wall thickness is not constant. In this way, a rapid spreading of the heat flow and the subsequent outflow into the surroundings is achieved.

[0011] Furthermore, the oil flows alongside the recesses and also perpendicularly to or transversely to the recesses when the reduction gear is in operation. In this way, the flow of the oil is disturbed and the thermal resistance from the oil to the housing is reduced.

[0012] In an advantageous design, each of the recesses extends longer in the direction perpendicular to the axial direction—that is, perpendicular to the axis of rotation of the input shaft—than in the axial direction. The advantage is that, with the input shaft vertically oriented, after upward injection, the oil flowing out in the vertical direction flows laterally through the recesses and thus flows in a disturbed manner.

[0013] In an advantageous design, the one or more areas are arranged below the oil level, particularly below the oil level that occurs when the reducer stops. This allows heat from the oil sump to be dissipated to the surrounding environment through the housing as efficiently and quickly as possible.

[0014] In an advantageous design, regularly spaced recesses are designed on the outer side of the housing component in the second region, and the wall thickness is constant in the second region.

[0015] In particular, the inner side of the housing component also features regularly spaced recesses, which, in contrast to the regularly spaced recesses on the outer side of the housing component, ensure a constant wall thickness. This design offers the advantage of both increased surface area and the ability to identifiablely form designs indicating the manufacturer's characteristics on the housing.

[0016] Preferably, the second region is arranged above the oil sump, that is, above the oil level that occurs when the oil is in a static state.

[0017] In an advantageous design, in the second region, each of the recesses extends longer in a direction perpendicular to the axial direction—that is, perpendicular to the axis of rotation of the input shaft—than in the axial direction. The advantage is that the recesses are elongated and thus allow for a disturbed flow of oil that is not parallel to the movement of the corresponding recess.

[0018] In an advantageous design, the housing component is connected to the gearbox cover, particularly in an oil-sealed manner, wherein the housing component and the gearbox cover together restrict the oil flow.

[0019] Specifically, at least one area of ​​the gearbox cover has regularly spaced recesses on its outer side, and the wall thickness is constant in this area.

[0020] In particular, the inner side of the reducer cover is designed with regularly spaced recesses, which, in contrast to the regularly spaced recesses on the outer side of the reducer cover, ensure a constant wall thickness. The advantage is that the increased heat capacity allows for rapid heat diffusion within the housing and also better smooths out temperature peaks.

[0021] In an advantageous design, reinforcing ribs are formed on the inside of the reduction gear cover, which cross one another,

[0022] In particular, corresponding recesses and elevations are designed between the reinforcing ribs. The advantage is that the oil flowing alongside the reinforcing ribs flows turbulently.

[0023] In an advantageous design, the wall thickness of the reduction gear cover fluctuates periodically along a first one of the reinforcing ribs, in particular periodically along the direction of maximum extension of the first reinforcing rib,

[0024] In particular, the inside of the first reinforcing rib is designed to be smooth, in particular flat. The advantage is that the reinforcing rib has a high thermal capacity and thus enables a diffusion of the heat flow.

[0025] In an advantageous design, the period length of the spatial profile of the wall thickness in the first region of the housing part is equal to the period length of the spatial profile of the wall thickness in the second region and / or to the period length of the spatial profile of the wall thickness along a first one of the reinforcing ribs of the reduction gear cover. The advantage is that the wall thickness can be designed constantly by means of a synchronous profile, i.e. a periodic profile with a constant phase reference.

[0026] In an advantageous design, the reduction motor has a reduction gear, an electric motor and an adapter flange, in particular an adapter flange arranged between the reduction gear and the electric motor,

[0027] In particular, the adapter flange has a rotationally symmetrical, annular base body shaped with respect to the rotational axis of the input shaft of the reduction gear, on which an axial projection is formed,

[0028] In particular, the axial projection is arranged on the side of the adapter flange facing away from the electric motor,

[0029] In particular, the radial distance region 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,

[0030] In particular, the region covered by the housing part in the axial direction overlaps the region covered by the axial projection in the axial direction, in particular in the circumferential angle region not covered by the axial projection and in the radial distance region covered by the axial projection,

[0031] In particular, the region covered by the housing part in the axial direction overlaps the region covered by the axial projection in the axial direction,

[0032] In particular, the axial direction is parallel to the rotational axis of the input shaft, the radial distance is the distance with respect to the rotational axis of the input shaft and / or the circumferential direction relates to this rotational axis of the input shaft,

[0033] or wherein the axial protrusion is designed to be interrupted in the circumferential direction, the housing part extending into the interrupted region.

[0034] The advantage is that the axial protrusion is designed to be as compact as possible, on the one hand, for the centering connection to the motor and the reduction gear, but on the other hand. Since centering requires at least a cylindrical, finely finished face on which the orientation takes place. According to the invention, however, the cylindrical face is interrupted in the circumferential direction, i.e. is not designed completely annular. The interrupted region can thus be covered by a subregion of the housing part, which surrounds the largest toothed part of the reduction gear, i.e. the gear wheel connected to the output shaft in a rotationally fixed manner, in a manner forming a housing.

[0035] Preferably, the interrupted circumferential angle region is less than 180°.

[0036] A further advantage of the invention is that the flange connection type towards the motor, i.e. the circular flange, differs from the flange connection type towards the reduction gear, e.g. the square flange. The hole pattern can also be used differently accordingly. For example, towards the reduction gear, a rectangular hole pattern can be used, while towards the motor a polygonal, i.e. more circular, hole pattern can be used.

[0037] Here, even the radial distance region covered by the holes of the hole pattern towards the motor can overlap with the radial distance region covered by the holes of the hole pattern towards the reduction gear. However, in the circumferential direction, all holes of the two hole patterns are spaced apart from one another. The holes of the two hole patterns are preferably designed to be through-going the adapter flange.

[0038] In particular, the first hole pattern used towards the reduction gear is arranged only in the circumferential angle region covered by the axial protrusion. In particular, the second hole pattern used towards the motor also overlaps the circumferential angle region covered by the interrupted region of the axial protrusion. The symmetry axes of the discrete rotational symmetries of the two hole patterns are therefore not congruent, but are spaced apart from one another. In this way, the adapter flange can be designed particularly compact. Because of the spacing of the symmetry axes, an interrupted region can be provided between the annular base body of the adapter flange and the housing part of the reduction gear.

[0039] In an advantageous design, the adapter flange is connected to a circular flange towards the motor and to a rectangular or square flange towards the reduction gear. The advantage is that different flange types with correspondingly different hole patterns and centering faces can be provided.

[0040] In an advantageous design, the adapter flange has an axially oriented first eye on its side facing the motor, through which a connecting element, such as a screw or bolt, projects, which also projects through a support flange of the motor,

[0041] The hole pattern of the first bore has discrete rotational symmetry, in particular higher than six-fold rotational symmetry, based on the rotational axis of the input shaft. The advantage is that the rotational axis of the rotor shaft of the electric machine is oriented centrally, in particular centrally, with respect to the adapter flange. A stable fixing of the adapter flange is thus achieved.

[0042] In an advantageous design variant, the adapter flange has an axially oriented second bore on the side thereof facing the reduction gear, which second bore extends through the axial protrusion of the adapter flange and the annular ring of the adapter flange,

[0043] wherein a connecting element, such as a screw or a bolt, extends through the second bore and is screwed into a threaded hole formed in the housing part,

[0044] In particular, the hole pattern of the second bore has discrete rotational symmetry, in particular two-fold rotational symmetry, based on a symmetry axis parallel to the rotational axis of the input shaft, which symmetry axis is spaced apart from the rotational axis. The advantage is that the reduction electric machine can be designed compactly, since the mechanical reduction gear-side interface, in particular the centering and fixing means, is moved and arranged in such a way that a region of interruption of the axial protrusion can be provided and can be at least partially filled by accommodation of a toothed part connected to the output shaft.

[0045] In an advantageous design variant, the adapter flange is centered on a receiving part of the reduction gear, in particular the adapter flange is oriented and centered coaxially to the rotational axis of the input shaft on the receiving part of the reduction gear,

[0046] wherein the receiving part is oriented, in particular centered, on the housing part of the reduction gear, in particular by means of a cylindrical centering flange,

[0047] In particular, the receiving part is connected to the housing part by means of a bolt,

[0048] In particular, the receiving part is held pressed against the housing part by the head of the bolt, which is screwed into an axially oriented threaded hole of the housing part. The advantage is that the adapter flange is centered on the receiving part, in which the bearing of the input shaft is received. Thus, not the housing part of the reduction gear, but the receiving part, which receives the bearing arrangement, is used for centering. The electric machine thus centers on the adapter flange, which faces the support flange of the electric machine, which in turn is centered on the receiving part, in which the bearing of the input shaft is centered. In this way, the electric machine, in particular its rotor shaft, which is supported by the bearing received in the support flange, is oriented coaxially to the input shaft of the reduction gear.

[0049] In an advantageous design variant, a bearing is received in the receiving part, the inner ring of which is respectively fitted onto the input shaft.

[0050] In an advantageous design, the annular ring is designed completely circumferentially, in particular without interruptions. The advantage is that a high stability can be achieved. Furthermore, a rotationally symmetrical hole pattern can be arranged completely towards the electric machine, so that the electric machine can still be fixed in the region of the interruptions. The reduction gear can also be fixed without interruptions, since the hole pattern can be arranged in the axial protrusion and thus a stable connection between the adapter flange and the housing part of the reduction gear can be established.

[0051] In an advantageous design, the maximum of the radial distance region covered by the axial protrusion has four local maxima in relation to the circumferential angle,

[0052] In particular, each circumferential angle region covered by the second eyelet contains a circumferential angle corresponding to a respective local maximum. The advantage is that the eyelets of the hole pattern facing the reduction gear are arranged in a radially wide region of the axial protrusion.

[0053] In an advantageous design, the axial protrusion has a finished surface towards the reduction gear, the minimum radial distance of which is constant in a subregion of the circumferential angle region covered by the axial protrusion,

[0054] In particular, the subregion covers more than 80% of the circumferential angle region covered by the axial protrusion. The advantage is that an exact centering can be achieved.

[0055] In an advantageous design, the cover part is connected to the receiving part, in particular sealingly by means of a sealing arranged in between, in particular a flat sealing,

[0056] wherein a shaft seal ring is received in the cover part, which seals towards the input shaft, in particular a sealing lip of the shaft seal ring works on a sealing surface designed on the input shaft. The advantage is that the input region, in particular the bearing structure of the input shaft, is closed oil-tightly. Furthermore, by fitting and connecting the cover part, a shaft seal ring which further improves the sealing is activated. Here, the cover part has a centering flange with which the cover part can be oriented on the receiving part. In this way, the shaft seal ring received in the cover part is centered coaxially to the input shaft of the reduction gear, although the bearing is received in the receiving part and thus the machining of the bearing seat can be carried out with the machine tool in only one process step.

[0057] In an advantageous design, the compression ring and the clamping ring are fitted on the input shaft, wherein the compression ring rests against a first bearing of the bearing,

[0058] wherein the clamping ring is connected to the input shaft in a force-locked / friction-locked manner,

[0059] In particular, the axially oriented bolts are supported on the clamping ring and are screwed into axially oriented threaded holes of the pressure ring, so that the bolts supported on the clamping ring press the pressure ring onto the first bearing, in particular onto the inner ring of the first bearing. The advantage is that a simple arrangement can be used to generate the bearing pressure.

[0060] In an advantageous design, the housing of the shaft-end pump is connected with the housing part, the intermediate shaft of the speed reducer is connected with the rotatable part of the shaft-end pump in a rotationally fixed manner, in particular drives the rotatable part. The advantage is that the oil can be passively conveyed, that is, in particular not with an electrically driven pump, but with a pump driven by the intermediate shaft rotating in operation.

[0061] In an advantageous design, the oil conveyed by the shaft-end pump from the oil sump reaches the bearing arranged further away from the intermediate shaft via a first channel arranged in the housing part, in particular via a first channel arranged in the housing part, which penetrates the housing part, and via a second channel, which penetrates the receiving part,

[0062] In particular, the first channel consists of a bore formed in the housing part and / or the second channel consists of a bore formed in the receiving part. The advantage is that passive lubrication of the bevel gear stage and in particular of its bearings is possible even if the input shaft is oriented vertically, that is, the rotational axis of the input shaft is oriented parallel to the direction of gravity.

[0063] In an advantageous design, a fourth channel is arranged in the receiving part, which is designed mirror-symmetrically to the second channel, in particular mirror-symmetrically with respect to a mirror plane containing the rotational axis of the input shaft. The advantage is that the shaft-end pump can alternatively be arranged on the other end of the intermediate shaft and thus there is the same type of channel structure. Optionally, even one shaft-end pump each can be provided on both ends of the intermediate shaft. Thus, the intermediate shaft, which rotates slower than the input shaft, can still be used to convey a large oil flow. Because a large oil flow can still be conveyed by two shaft-end pumps, which are even driven slower.

[0064] In an advantageous design, a fourth channel is arranged in the receiving part, which is designed mirror-symmetrically to the second channel, in particular mirror-symmetrically with respect to a mirror plane containing the rotational axis of the input shaft. The advantage is that the shaft-end pump can alternatively be arranged on the other end of the intermediate shaft and thus there is the same type of channel structure. Optionally, even one shaft-end pump each can be provided on both ends of the intermediate shaft. Thus, the intermediate shaft, which rotates slower than the input shaft, can still be used to convey a large oil flow. Because a large oil flow can still be conveyed by two shaft-end pumps, which are even driven slower.

[0065] In an advantageous design, the first channel has a first blind hole which is oriented radially and is formed in the housing part, which first blind hole opens into a second blind hole which is oriented axially and is formed in the housing part and is closed with a closure plug relative to the surroundings, which second blind hole intersects a third hole which is oriented radially and runs through the housing part, which third hole opens into a fourth hole which is oriented radially and is formed in the receiving part, which fourth hole intersects a fifth blind hole which is oriented axially and is formed in the receiving part,

[0066] In particular, the fourth hole is only incompletely closed towards 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 arranged below the fourth hole of the two bearings of the input shaft,

[0067] In particular, the first channel has an outlet which is located above the bearings of the input shaft. The advantage is that the upper of the bearings is supplied with oil via the outlet and the lower of the bearings is supplied with oil via the plug which is arranged in an oil-permeable manner.

[0068] In an advantageous design, the first channel comprises a first hole, a second hole, a third hole, a fourth hole and a fifth hole. The advantage is that a simple production is possible by forming the holes. It is particularly advantageous, however, to use blind holes, since these do not require a closure plug.

[0069] In an advantageous design, the receiving part has four radial holes which run through the receiving part and are spaced apart from one another in the circumferential direction, said four radial holes being arranged at the same axial location, i.e. in particular covering the same axial region. The advantage is that at least one of said holes serves as an inlet for oil and is therefore filtered and delivers oil into the gap region between the input shaft and the receiving part, so that the oil flows downwards along the input shaft on the two bearings of the input shaft which are arranged lower in the direction of gravity.

[0070] In an advantageous design, the input shaft is connected in a rotationally fixed manner to a bevel pinion which meshes with a bevel gear which is connected in a rotationally fixed manner to the intermediate shaft,

[0071] wherein the intermediate shaft is connected in a rotationally fixed manner to a helical spur gear which meshes with a gear which is connected in a rotationally fixed manner to the output shaft of the reduction gear,

[0072] In particular, the spacer, which is held in a form-locking manner by a bolt screwed into the input shaft, limits the bevel pinion in the axial direction. The advantage is that the input bevel gear stage is followed by a spur gear stage. The gears of the spur gear stage can be designed as helical toothing. A low-noise operation is thus achieved.

[0073] Further advantages are given by the dependent claims. The application is not restricted to the combination of features of the claims. Further reasonable combination possibilities of the claims and / or individual features of the claims and / or features of the description and / or features of the drawings are available to the person skilled in the art, in particular from the technical problem presented and / or by comparison with the prior art. BRIEF DESCRIPTION OF DRAWINGS

[0074] The application is now explained in detail on the basis of the schematic drawings:

[0075] In Figure 1 a reduction gear with an adapter flange 3 for connection to an electric machine 120 is shown in an oblique view.

[0076] In Figure 2 the reduction gear is shown from another viewing direction.

[0077] In Figure 3 the reduction gear is shown in a cutaway view.

[0078] In Figure 4 another cutaway view of the reduction gear is shown.

[0079] In Figure 5 a perpendicular section of the reduction gear is shown.

[0080] In Figure 6 a perpendicular section of the reduction gear with an adapter flange 3 is shown. Figure 1 a corresponding top view.

[0081] In Figure 7 a reduction gear with an adapter flange 3 is shown in an oblique view, which is shown in an exploded view.

[0082] In Figure 8 the adapter flange 3 is shown in an oblique view from a first viewing direction.

[0083] In Figure 9 the adapter flange 3 is shown in an oblique view from a second viewing direction.

[0084] In Figure 10 a cutaway view of the reduction gear is shown, so that the input area of the reduction gear is visible.

[0085] In Figure 11In the figure, the shaft, the toothed components and the bearings of the speed reducer are shown in an oblique view, wherein the housing component 1 of the speed reducer and the lubricating oil of the speed reducer are omitted.

[0086] In the figure, the shaft, the toothed components and the bearings of the speed reducer are shown in an oblique view, wherein the housing component 1 of the speed reducer and the lubricating oil of the speed reducer are omitted. Figure 12 In the figure, the shaft, the toothed components and the bearings of the speed reducer are shown in an oblique view, wherein the housing component 1 of the speed reducer and the lubricating oil of the speed reducer are omitted. DETAILED DESCRIPTION

[0087] As shown in the figures, a mating flange 3 is arranged between the motor 120 and the housing component 1 of the speed reducer, so that the motor 120 can be centered on the mating flange and can be mounted to the mating flange 3 by means of bolts.

[0088] The mating flange 3 is centered on the housing component 1 and is connected to the housing component 1 by means of bolts.

[0089] The mating flange 3 has a circular outer shape on its side facing the motor 120. In particular, the largest outer circumference of the mating flange 3 is designed to be circular, in particular to be a cylindrical outer contour.

[0090] The mechanical interface facing the motor 120, in particular the mechanical interface having the centering ring and the hole pattern, has rotational symmetry, in particular rotational symmetry based on the rotational axis of the input shaft 4. The rotational symmetry is at least discrete, but can also be designed to be continuous.

[0091] The radial distance is always based on the rotational axis of the input shaft 4 here. Likewise, the axial direction is parallel to the rotational axis of the input shaft 4. The circumferential direction is also based on the rotational axis of the input shaft 4.

[0092] The mating flange 3 has an axial protrusion 90 on its side facing the speed reducer housing 1, which protrudes axially towards the housing component 1, but is interrupted in the circumferential direction by a thinned wall region 92. Here, the thinned wall region 92 has a smaller extent in the axial direction, in particular a smaller wall thickness, compared to the circumferential angular region covered by the axial protrusion 90.

[0093] That is, the mating flange 3 preferably has an annular base body which is designed to be rotationally symmetrical about the rotational axis of the input shaft 4 of the speed reducer and on which the axial protrusion 90 is formed on the speed reducer side, but which is not rotationally symmetrical, but is interrupted in a circumferential angular region. The housing component 1, in particular the arch of the housing component 1 which at least partially encloses the output gear 113 in a housing-like manner, projects into this interrupted circumferential angular region, wherein the radial distance region covered by the housing component 1 in this interrupted region, that is to say in this circumferential angular region and in the region covered by the base body in the axial direction, overlaps the radial distance region covered by the base body.

[0094] The housing part 1 thus projects into the interrupted region of the axial protrusion 90.

[0095] An axially oriented eyelet 91 is formed in the axial protrusion 90, in particular the eyelet forms a rectangular, in particular square, hole pattern.

[0096] The bolts for connecting the housing part 1 with the adapter flange 3 are thus arranged in a rectangular arrangement.

[0097] That is to say, a square flange can be used towards the reduction gear, while a circular flange can be used towards the electric machine 120.

[0098] The axial protrusion 90 only covers a part of the entire circumferential angle region. The radial distance of the maximum coverage has four local maxima in relation to the circumferential angle.

[0099] The circumferential angle regions covered by the respective eyelets 91 each contain the circumferential angle values of the respective maxima.

[0100] The respective eyelets 91 are thus each arranged in a radially expanded region of the axial protrusion 90.

[0101] The axial protrusion 90 has an inner cylindrical surface region on its inner circumferential portion, that is to say at its smallest radial distance, which, however, is interrupted in the circumferential angle region not covered by the axial protrusion 90.

[0102] The inner circumferential portion serves as a receiving portion for centring the receiving part 41 of the reduction gear. The inner cylindrical surface region is oriented coaxially to the rotational axis of the input shaft 4.

[0103] Furthermore, the axial protrusion has a finely finished, axially protruding toroid in the circumferential angle region covered by the axial protrusion 90.

[0104] By means of the toroid, the adapter flange 3 rests on the finely finished flat surface regions of the housing part 1. Here, a respective axially oriented hole, in particular a threaded hole, is formed in each of the finely finished flat surface regions, wherein the bolts pass through the eyelets 91 and are screwed into the threaded holes 71 formed in the finely finished flat surface regions of the housing part 1.

[0105] The toroid of the axial protrusion 90 and the surface region in which the eyelets 91 are formed are located in the same axial position. This axial position is the position farthest from the electric machine 120, which is covered by the adapter flange 3.

[0106] The thinned wall region 92 of the adapter flange 3 lies on the arch, in particular the elevation, of the housing part 1 or at least only has a small spacing. The arch at least partially surrounds the gearwheel 113 connected with the output shaft in a housing-forming manner.

[0107] The output shaft 5 is oriented perpendicular to the input shaft 4.

[0108] The gearwheel 113, which is connected to the output shaft 5 in a rotationally fixed manner, together with the arch covers an area in the axial direction, that is to say in a direction perpendicular to the rotational axis of the input shaft, which area includes the area covered by the bearing 47 of the input shaft 4.

[0109] The electric machine 120 has a stator housing which is connected on both sides axially to a support flange which is designed as a circular flange. Each of the two support flanges receives a bearing which is fitted onto the rotor shaft of the electric machine 120. The rotor shaft is thus supported in a rotatable manner by the two bearings which are received in the support flanges.

[0110] The two support flanges are designed as circular flanges. They thus have an essentially circular peripheral portion. The hole pattern for connecting the first of the two support flanges to the adapter flange 3 has discrete rotational symmetry, wherein the axis of rotational symmetry corresponds to the rotational axis of the rotor shaft, in particular also of the input shaft 4 which is arranged coaxially to the rotor shaft. The hole pattern which the first support flange of the adapter flange 3 has towards the electric machine 120 likewise has this discrete rotational symmetry.

[0111] The bearing 47 is received in a receiving part 41 which has a radially outwardly projecting, circumferentially encircling flange which is pressed onto the housing part 1 by means of screws which are screwed into axially oriented threaded holes of the housing part 1.

[0112] Here, a step is milled into the flange and thus designed for centring on the housing part 1.

[0113] The bearing 47 is fitted onto the input shaft 4 which is thus supported in a rotatable manner.

[0114] The cover part 46 is pressed onto the receiving part 47 by means of screws which are screwed into threaded holes of the receiving part 47, in particular by means of the screw heads of the screws. A shaft seal 45 is received in the cover part 46 which seals the cover part 46 towards the input shaft 4.

[0115] A press ring 52 and a clamping ring 50 are fitted onto the input shaft 4 which abut against the first bearing in the bearing 47, wherein the clamping ring 50 is connected to the input shaft 4 in a force-locking manner. Axially oriented screws 51 are supported on the clamping ring 50 and are screwed into axially oriented threaded holes of the press ring 52, so that the screws which are supported on the clamping ring 50 press the clamping ring 52 against the first bearing 47. In particular, the press ring 52 is pressed onto the inner ring of the first bearing 47 here.

[0116] The input shaft 4 penetrates the cover part 46. The input shaft 4 is connected in a rotationally fixed manner with a bevel pinion 49, the toothing of which meshes with the toothing of the gear wheel 48, in particular a bevel gear wheel.

[0117] The outer ring of the first bearing 47 rests on a shoulder of the receiving part 41.

[0118] The bevel pinion 49 is fitted onto the conical end region of the input shaft 4 and is axially fixed by means of a washer, which is pressed onto the end side of the input shaft 4 by a bolt that is centrally screwed into the end side of the input shaft 4. Furthermore, the bevel pinion 49 is connected in a force-locked and / or form-locked manner, in particular by means of a key connection.

[0119] An axially protruding, circumferentially encircling centering flange is formed on the cover part 46, which centering flange is oriented and centered on a centering seat formed on the receiving part 41.

[0120] The bevel pinion 49 meshes with the toothing of the gear wheel 48, in particular a bevel gear wheel.

[0121] The gear wheel 48 is connected in a rotationally fixed manner with an intermediate shaft 111, which is rotatably supported by means of bearings received in the housing part and is connected in a rotationally fixed manner with a toothed portion 112, which meshes with a toothed portion of a gear wheel 113, which is connected in a rotationally fixed manner with the output shaft 5.

[0122] The reduction gear according to the application, which is preferably two-stage, thus has an input bevel gear stage, which is followed by a cylindrical gear stage arranged on the output side. The toothing of the cylindrical gear stage preferably each has a non-zero angle of inclination.

[0123] The intermediate shaft 111 is connected with the shaft end pump 100. Thus, although the shaft end pump is not driven by the rapidly rotating input shaft 4, but by the intermediate shaft 111, which is at least rotated faster than the output shaft 5.

[0124] The oil level in the interior space of the reduction gear covers or reaches the pinion toothing. However, the two bearings 47 of the input shaft 4 are arranged above the oil level and thus are not lubricated after a long standstill of the reduction gear.

[0125] Thus, as soon as the reduction gear is running, the shaft end pump 100 driven by the intermediate shaft 111 pumps oil from the oil reservoir arranged below the oil level to a position above the bearings 47, so that the bearings 47 are lubricated and the shaft seal 40 also does not run dry.

[0126] The input shaft 4 is parallel to the normal direction of the oil pool surface, in particular when the reduction gear is stationary for a longer period of time.

[0127] The other bearings, toothing parts (112, 49) and gears (48, 113) are always at least partially immersed in the oil pool of the reduction gear.

[0128] As shown in Figure 10 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 bore and opens into an axially oriented bore 102 of the housing part 1, which is likewise machined from the outside as a blind bore and is closed on its end facing the electric machine 120 with a closure plug 105.

[0129] A radially oriented bore 103 through the housing part 1 intersects the bore 102 and opens into a radial bore 108 formed in the receiving part 41, which is closed toward the input shaft 4 with a plug 107, which is not completely tight, but lets a small amount of oil through, which then reaches the bearing 47 below, that is to say further away from the electric machine 120, in the gap between the housing part 1 and the input shaft 4.

[0130] An axially oriented blind bore 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 on the end of the receiving part 41 facing the cover part 46 and supplies the bearing 47 above, that is to say facing the electric machine 120. The second bearing 47 arranged below the first bearing 47 is consequently supplied as well.

[0131] The two bearings 47 are preferably designed as radial thrust bearings.

[0132] The receiving part 41, which is connected to the housing part 1 oil-tight, together with the cover part 46, which is connected to the receiving part 41 oil-tight, encloses the interior space region of the reduction gear.

[0133] When the reduction gear is running and thus when the intermediate shaft 111 is in rotational motion, the oil is delivered by the shaft end pump 100 counter to the direction of gravity and thus lubricates the bearings 47 with oil. In addition, the oil flowing past the bearings 47 absorbs the loss heat, which is then conducted from the oil pool to the surroundings.

[0134] In order to achieve as small a thermal resistance as possible from the oil pool toward the surroundings or at least toward the housing part 1, regions with recesses 30, in particular regularly spaced from one another, are designed on the inside of the housing part 1.

[0135] In these regions, the wall thickness is preferably not constant, but these regions are smoothly, in particular flatly, designed on their outside.

[0136] The wall thickness thus varies in these regions in synchronism with the recesses 30.

[0137] Here, each of the recesses 30 extends longer in a direction perpendicular to the axial direction, i.e. perpendicular to the axis of rotation of the input shaft 4, than in the axial direction.

[0138] Preferably, the recesses 30 are arranged below the oil level and thus provide an increased surface on the inner side, so that the heat transfer resistance from the oil to the housing part 1 is reduced and the heat can be absorbed in the regions arranged between the recesses 30, in particular by the flat structure of the respective region on the outer side, thickened, in particular due to the larger heat capacity generated by the thickening. From there, the heat is then diffused in the housing part 1 and conducted to the surroundings.

[0139] In other regions, recesses 2 are provided on the outer side of the housing part, wherein the wall thickness is constant in these other regions. Accordingly, corresponding recesses are formed not only on the outer side, in particular on the outer side with recesses 2 regularly spaced apart from one another, but also on the inner side.

[0140] Here, each of the recesses 2 likewise extends longer in a direction perpendicular to the axial direction, i.e. perpendicular to the axis of rotation of the input shaft 4, than in the axial direction.

[0141] Accordingly, the recesses 2 can be formed on the housing part 1 in order to achieve a particular, source-indicating design impression. Conversely, the recesses 30 formed only on the inner side are not used for the design impression, but for improving the heat dissipation.

[0142] On the underside of the reduction gear, the interior space of the reduction gear is closed by means of a reduction gear cover 31, which likewise has recesses 2 and a constant wall thickness, but wherein mutually intersecting reinforcing ribs 32 are formed on the inner side of the reduction gear cover. Accordingly, the reduction gear cover 31 is on the one hand rigid and also conveys a source-indicating design impression, wherein the underside of the oil sump is thus stabilized, since the flowing oil has to overcome not only the reinforcing ribs 32, but also the recesses and elevations between the reinforcing ribs 32. Accordingly, less laminar flow, more disturbed flow is formed in the oil sump when the oil moves. The heat transfer from the oil to the reduction gear cover 31 is thus also improved thereby.

[0143] In the receiving part 41, a radial hole 43 is arranged which runs through the receiving part 41 spaced apart from the radial hole 108 in the circumferential direction, into which a blind hole formed in the receiving part, which projects out of the receiving part 41 towards the oil sump, opens axially. Accordingly, it is possible to achieve an oil discharge from the spatial region located between the input shaft and the receiving part. This oil discharge serves for pressure relief in particular in the case of an overpressure in this region.

[0144] The radial bore 43 is closed towards the radial outside by means of the housing part 1, into which the receiving part 41 projects. The receiving part 41 has another such pressure relief in mirror-symmetrical relation with respect to a plane of symmetry containing the axis of rotation of the input shaft.

[0145] That is to say, the receiving part 41 has, in this way, four radial bores through the receiving part at the same axial position, which are spaced apart from one another in the circumferential direction.

[0146] In other embodiments according to the application, the bevel pinion 49 is designed in one piece, in particular integrally, with the input shaft.

[0147] List of reference signs:

[0148] 1 housing part

[0149] 2 recess

[0150] 3 adapter flange

[0151] 4 input shaft

[0152] 5 output shaft

[0153] 30 recess

[0154] 31 reducer cover

[0155] 32 reinforcing rib

[0156] 40 shaft seal

[0157] 41 receiving part

[0158] 42 screw

[0159] 43 radial bore

[0160] 44 axial bore

[0161] 45 shaft seal

[0162] 46 cover part

[0163] 47 bearing, in particular conical roller bearing

[0164] 48 gearwheel, in particular bevel gearwheel

[0165] 49 bevel pinion

[0166] 50 clamping ring

[0167] 51 screw

[0168] 52 compression ring

[0169] 60 screw

[0170] 61 first eyelet

[0171] 71 hole, in particular threaded hole

[0172] 90 axial protrusion

[0173] 91 second eyelet

[0174] 92 thinned wall region

[0175] 100 shaft end pump

[0176] 101 radial hole

[0177] 102 axial hole

[0178] 103 radial hole

[0179] 104 closure plug

[0180] 105 closure plug

[0181] 106 axial hole

[0182] 107 plug

[0183] 108 radial hole

[0184] 111 intermediate shaft

[0185] 112 tooth

[0186] 113 gear wheel

[0187] 120 electric machine

Claims

1. A gear motor comprising a gear reducer having a housing with a housing part which at least partially surrounds toothed parts and oil in a manner forming the housing, characterized in that - the wall thickness of the housing part fluctuates periodically in one or more regions of the housing part, in that - in the one or more regions, the outer surface is designed to be smooth, - or in that on the inner side of the housing part there is provided a region with recesses regularly spaced apart from one another, the wall thickness varying in the one or more regions in synchronism with the recesses, in that the gear motor has a gear reducer, an electric motor and an adapter flange arranged between the gear reducer and the electric motor, so that the electric motor can be centered on the adapter flange and can be mounted on the adapter flange by means of bolts, in that the adapter flange has a rotationally symmetrically shaped, annular base body with respect to the rotational axis of the input shaft of the gear reducer, on which base body an axial projection is formed, in that the axial projection is arranged on the side of the adapter flange facing away from the electric motor, in that the radial distance region 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, in that the region covered by the housing part in the axial direction overlaps the region covered by the axial projection in the axial direction, in that the axial direction is parallel to the rotational axis of the input shaft, the radial distance is the distance with respect to the rotational axis of the input shaft, and the circumferential direction relates to this rotational axis of the input shaft, in that the axial projection is designed to be interrupted in the circumferential direction, the housing part extending into the region of the interruption.

2. The gear motor according to claim 1, characterized in that - each of the recesses extends longer in a direction perpendicular to the axial direction than in the axial direction.

3. The gear motor according to claim 1 or 2, characterized in that - the one or more regions are arranged below the oil level of the oil.

4. The gear motor according to claim 1 or 2, characterized in that - in a second region, recesses regularly spaced apart from one another are designed on the outer side of the housing part and the wall thickness is constant in the second region, - recesses regularly spaced apart from one another are also designed on the inner side of the housing part, these recesses being spaced apart from the recesses designed on the outer side of the housing part in such a way that the wall thickness is constant.

5. The gear motor according to claim 4, characterized in that - in the second region, each of the recesses extends longer in a direction perpendicular to the axial direction than in the axial direction.

6. The gear motor according to claim 1 or 2, characterized in that - the housing part is connected with a reducer cover, wherein the housing part together with the reducer cover confines the oil, - in at least one region of the reducer cover, recesses regularly spaced apart from one another are designed on the outer side of the reducer cover and the wall thickness is constant in this region, - recesses regularly spaced apart from one another are also designed on the inner side of the reducer cover, these recesses being spaced apart from the recesses designed on the outer side of the reducer cover in such a way that the wall thickness is constant.

7. The gear motor according to claim 6, characterized in that - the recesses designed on the outer side of the reducer cover are designed to be interrupted in the circumferential direction, the housing part extending into the region of the interruption. ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ On the inner side of the reduction gear cover, reinforcing ribs are formed which cross one another, Between the reinforcing ribs, corresponding recesses and elevations are designed.

8. The reduction gear motor according to claim 7, characterized in that The wall thickness of the reduction gear cover fluctuates periodically along a first one of the reinforcing ribs, wherein the inner side of the first reinforcing rib is designed to be smooth.

9. The reduction gear motor according to claim 8, characterized in that The period length of the space of the curve of the wall thickness in the first region of the housing part is equal to the period length of the space of the curve of the wall thickness in the second region and / or to the period length of the space of the curve of the wall thickness along a first one of the reinforcing ribs of the reduction gear cover.

10. The reduction gear motor according to claim 1, characterized in that The adapter flange is connected to the motor with a circular flange and to the reduction gear with a rectangular or square flange, and / or The adapter flange has an axially oriented first eyelet on its side facing the motor, through which the connecting element projects, the connecting element also projecting through a support flange of the motor, wherein the hole pattern of the first eyelet has discrete rotational symmetry based on the rotational axis of the input shaft, and / or The adapter flange has an axially oriented second eyelet on its side facing the reduction gear, which second eyelet penetrates through an axial protrusion of the adapter flange and an annular base body of the adapter flange, wherein the connecting element projects through the second eyelet and is screwed into a threaded hole formed in the housing part, The hole pattern of the second eyelet has discrete rotational symmetry based on a parallel symmetry axis spaced apart from the rotational axis of the input shaft.

11. The reduction gear motor according to claim 10, characterized in that The adapter flange is centered on a receiving part of the reduction gear, wherein the receiving part is oriented on a housing part of the reduction gear, The receiving part is connected to the housing part by means of bolts, The receiving part is held pressed against the housing part by the bolt heads of the bolts screwed into axially oriented threaded holes of the housing part, and / or A bearing is received in the receiving part, the inner ring of the bearing being respectively fitted on the input shaft, and / or The annular base body is designed completely annularly in the circumferential direction.

12. The reduction gear motor according to claim 11, characterized in that The maximum of the radial distance region covered by the axial protrusion has four local maxima in relation to the circumferential angle, Each circumferential angle region covered by the second eyelet contains a circumferential angle corresponding to a respective local maximum, and / or The axial protrusion has a finished face facing the reduction gear, the minimum radial distance of which is constant in a subregion of the circumferential angle region covered by the axial protrusion, which subregion covers more than 80% of the circumferential angle region covered by the axial protrusion.

13. The reduction gear motor according to claim 1 or 2, characterized in that A cover part is connected to the receiving part, wherein a shaft seal ring is received in the cover part, which seals against the input shaft, and / or A compression ring (52) and a clamping ring (50) are fitted on the input shaft, wherein the compression ring (52) abuts against a first one of the bearings (47), wherein the clamping ring (50) is connected to the input shaft (4) in a force-locked manner, axially oriented bolts (51) are supported on the clamping ring (50) and are screwed into axially oriented threaded holes of the compression ring (52), so that the bolts supported on the clamping ring (50) press the compression ring (52) onto the first bearing (47), and / or the housing of the shaft-end pump is connected with the housing part, the intermediate shaft of the reduction gear is connected with the rotatable part of the shaft-end pump in a rotationally fixed manner, and / or the oil delivered by the shaft-end pump from the oil sump passes through a first channel arranged in the housing part and through a second channel to a bearing arranged further away from the intermediate shaft, the first channel opening into a second channel which penetrates the receiving part, the first channel being arranged in the housing part and penetrating the housing part, the first channel consists of a hole formed in the housing part, and / or the second channel consists of a hole formed in the receiving part, and / or a third channel is arranged in the housing part, which third channel is designed as a mirror image symmetrical to the first channel with respect to a mirror plane containing the rotational axis of the input shaft, and / or a fourth channel is arranged in the receiving part, which fourth channel is designed as a mirror image symmetrical to the second channel with respect to a mirror plane containing the rotational axis of the input shaft.

14. Reducing gear according to claim 13, characterized in that the first channel has a first radially oriented hole formed in the housing part, which first hole opens into a second axially oriented hole formed in the housing part, which second hole is closed with respect to the surroundings by means of a closure plug, which second hole intersects a third radially oriented hole which penetrates the housing part, which third hole opens into a fourth radially oriented hole formed in the receiving part, which fourth hole intersects a fifth axially oriented hole formed in the receiving part, the fourth hole is only incompletely closed towards 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 out of the fourth hole, past the plug, in the axial direction between the bearings of the input shaft, to supply the bearing arranged below the fourth hole among the two bearings of the input shaft, the first channel has an outlet above the bearings of the input shaft, the first channel comprises the first hole, the second hole, the third hole, the fourth hole and the fifth hole, the receiving part has four radially oriented holes which penetrate the receiving part and which are spaced apart from one another in the circumferential direction, said four radially oriented holes being arranged at the same axial location, and / or the input shaft is connected in a rotationally fixed manner with a bevel pinion which meshes with a bevel wheel which is connected in a rotationally fixed manner with the intermediate shaft, wherein the intermediate shaft is connected in a rotationally fixed manner with a helical spur gear which meshes with a gear wheel which is connected in a rotationally fixed manner with the output shaft of the reduction gear, a washer held in a form-locked manner by a bolt screwed into the input shaft limits the bevel pinion in the axial direction.

Images