CN111706665A

CN111706665A - Geared motor including a speed reducer having an input shaft and a housing

Info

Publication number: CN111706665A
Application number: CN202010703791.XA
Authority: CN
Inventors: 高琼华
Original assignee: Sew Tianjin Transmission Equipment Co ltd
Current assignee: Sew Tianjin Transmission Equipment Co ltd
Priority date: 2020-07-21
Filing date: 2020-07-21
Publication date: 2020-09-25

Abstract

The invention relates to a geared motor comprising a gear unit having an input shaft and a housing, which has a housing part, a receiving part and a cover part, and in particular a gear unit cover, wherein the housing at least partially encloses the toothed member and the oil in a manner forming a housing, the input shaft being rotatably supported by two bearings received in the receiving member, wherein, the shell of the shaft end pump is connected with the shell component, the intermediate shaft of the speed reducer is connected with the rotatable component of the shaft end pump in a relative rotation-proof way, the oil delivered by the shaft-end pump from the oil sump passes through a first passage arranged in the housing part, in particular through a first passage arranged in the housing part and extending through the housing part, and through a second passage to a bearing arranged further away from the intermediate shaft, the first passage opening into a second passage extending through the receiving part.

Description

Geared motor including a speed reducer having an input shaft and a housing

Technical Field

The present invention relates to a reduction motor including a reduction gear having an input shaft and a housing.

Background

It is generally known that a reduction gear of a reduction motor has a shaft rotatably supported by a bearing and a toothed member.

Disclosure of Invention

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

According to the invention, the object is achieved in a geared motor according to the features given in claim 1.

An important feature of the invention in the case of a reduction gear is that the reduction gear has an input shaft and a housing with a housing part, a receiving part and a cover part, and in particular a reduction gear cover, wherein the housing at least partially encloses the toothed part and the oil in such a way that it forms a housing,

wherein the input shaft is rotatably supported by two bearings received in the receiving part, in particular wherein the inner rings of the two bearings are slipped over the input shaft,

wherein the housing of the shaft-end pump is connected to the housing part, the intermediate shaft of the gear unit is connected in a rotationally fixed manner to a rotatable part of the shaft-end pump, in particular drives the rotatable part,

wherein the oil delivered by the shaft-end pump from the oil sump passes through a first passage arranged in the housing part, in particular through a first passage arranged in the housing part and extending through the housing part, and through a second passage to a bearing arranged further away from the intermediate shaft, the first passage opening into a second passage extending through the receiving part,

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 the oil can be delivered by means of a passive pump, i.e. a pump without its own separate power supply. Since the pump does not need its own motor for driving the pump, but is driven by the intermediate shaft of the gear unit. At a standstill, however, the bearings of the input shaft are therefore not lubricated by the oil delivered by the pump. Since the bearings of the input shaft can be arranged above the oil level, i.e. above the oil sump. In this way, during installation, the input shaft, which is mounted in the receiving part by means of the bearing, can be inserted as a preassembled unit into the recess of the housing part. Here, the channels are also connected. Since the passage in the receiving part and the passage in the housing part are likewise connected to one another when the receiving part is connected to the housing part.

Thus, a preassembled unit with a receiving part containing the input shaft and its bearing arrangement can be introduced into the housing part and can subsequently be connected by means of bolts. Here, the two channels are already present and, upon connection, the outlets of the two channels are aligned with each other, thereby establishing a connection of the two channels. A flat seal can be inserted between the receiving part and the housing part, so that the housing part and the receiving part are connected in an oil-tight manner when the screw is tightened.

The insertion of the preassembled unit must be carried out with care, since during the insertion, a bevel pinion arranged on the input shaft and connected in a rotationally fixed manner meshes with a gear wheel which is connected in a rotationally fixed manner to an intermediate shaft which drives the shaft-end pump and is rotatably mounted by means of a further bearing, which is fitted on the intermediate shaft and accommodated in the housing part.

The shaft end pump is preferably arranged on the outside of the housing part.

The branches of the second channel are preferably closed by means of a plug, but only in the following manner: the oil can also pass through, i.e. not be prevented by the plug from flowing sideways. In this way, oil can be fed from the branch into the spatial region arranged axially between the two bearings of the input shaft and can therefore be fed to the bearings of the bearing arrangement of the input shaft which are arranged further down.

The bevel pinion and gear are disposed at least partially below the oil level. Therefore, even at the time of shutdown, oil is present in the meshing area.

In an advantageous embodiment, the housing of the shaft-end pump is connected to the housing part, and the intermediate shaft of the gear unit is connected in a rotationally fixed manner to a rotatable part of the shaft-end pump, in particular drives the rotatable part. The advantage of this is that the oil can be delivered passively, i.e. in particular not by an electrically driven pump but by a pump driven by an intermediate shaft which rotates during operation.

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

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. The advantage of this is that passive lubrication of the bevel gear stage and in particular of its bearings is achieved even if the input shaft is oriented vertically, that is to say the axis of rotation of the input shaft is oriented parallel to the direction of gravity.

In an advantageous embodiment, a third channel is arranged in the housing part, which third channel is designed mirror-symmetrically to the first channel, in particular with respect to a mirror-mirror image containing the rotational axis of the input shaft. The advantage of this is that the shaft end pump can be arranged alternatively on the other end of the intermediate shaft and therefore the same type of channel structure is present. Alternatively, even one shaft end pump each can be arranged 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. Since a larger oil flow can be delivered by both shaft end pumps, even if driven slower.

In an advantageous embodiment, a fourth channel is arranged in the receiving part, which fourth channel is designed mirror-symmetrically to the second channel, in particular with respect to a mirror plane containing the rotational axis of the input shaft. The advantage of this is that the shaft end pump can be arranged alternatively on the other end of the intermediate shaft and therefore the same type of channel structure is present. Alternatively, even one shaft end pump each may 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. Since a large oil flow can still be delivered by the two shaft-end pumps, even if they are driven more slowly.

In one advantageous embodiment, the first channel has a radially oriented first blind hole formed in the housing part, which opens into an axially oriented second blind hole formed in the housing part and closed off with respect to the surroundings by means of a closing plug, which second blind hole intersects a radially oriented third bore running through the housing part, which third bore opens into a radially oriented fourth bore formed in the receiving part, which fourth bore intersects an axially oriented fifth blind hole formed in the receiving part,

in particular wherein the fourth bore is only incompletely closed off 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 oil delivered by the shaft end pump passes from the fourth bore, beside the plug, flows out in the axial direction between the bearings of the input shaft, supplies the bearing of the input shaft which is arranged below the fourth bore with oil,

in particular wherein the first passage has an outlet located above the bearing of the input shaft. This has the advantage that the upper one of the bearings is supplied with oil through the outlet and the lower one of the bearings is supplied with oil through the plug arranged in an oil-permeable manner.

In an advantageous embodiment, the first channel comprises a first bore, a second bore, a third bore, a fourth bore and a fifth bore. This has the advantage that simple manufacture is possible by forming the holes. However, it is particularly advantageous to use blind holes, since these do not require a closing plug.

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

In one advantageous embodiment, the gear unit has a housing with a housing part which at least partially surrounds the toothed part and the oil in such a way that it forms a housing,

wherein

The wall thickness of the housing part periodically fluctuates in one or more regions of the housing part, in particular in a linear direction,

in the region or regions, the outer surface is designed to be smooth, in particular flat,

or on the inside of the housing part, in particular on the oil-facing surface and/or the inner surface, there are regions with recesses, in particular regularly spaced recesses, in particular wherein the wall thickness varies in synchronism with the recesses in the region or regions.

This has the advantage that the inner surface is enlarged by the recess and thus the heat transfer resistance from the oil to the housing is reduced. Furthermore, with a smooth, in particular flat, outer surface, although the wall thickness is not constant, the heat capacity for diffusing the heat flowing into the housing increases. In this way, rapid diffusion of the heat flow and subsequent outflow into the surroundings is also possible.

Furthermore, when the retarder is in operation, the oil flows alongside the recess and also perpendicular or transverse to the recess. In this way, the flow of oil is disturbed, and thus the resistance to heat transfer from the oil to the casing is reduced.

In an advantageous embodiment, each of the recesses extends longer in a direction perpendicular to the axial direction, i.e. perpendicular to the axis of rotation of the input shaft, than in the axial direction. This has the advantage that, after upward injection with the input shaft oriented vertically, the oil flowing out in the vertical direction flows transversely to the recess and thus in a disturbed manner.

In an advantageous embodiment, the one or more regions are arranged below the oil level of the oil, in particular below the oil level which occurs when the gear unit is shut down. This has the advantage that heat from the oil sump can be discharged through the housing to the surroundings as efficiently and quickly as possible.

In an advantageous embodiment, recesses regularly spaced apart from one another are formed on the outside of the housing part in the second region and the wall thickness is constant in the second region,

in particular, recesses which are regularly spaced apart from one another are also formed on the inner side of the housing part, which recesses are spaced apart from recesses which are regularly spaced apart from one another and are formed on the outer side of the housing part in such a way that the wall thickness is constant. This has the advantage that, on the one hand, a surface enlargement is achieved and, on the other hand, a design which indicates the characteristics of the manufacturer can be formed in a recognizable manner on the housing.

Preferably, the second region is arranged above the oil sump, i.e. above the oil level that occurs when in a stationary state.

In an advantageous embodiment, in the second region, each of the recesses extends longer in a direction perpendicular to the axial direction, i.e. perpendicular to the axis of rotation of the input shaft, than in the axial direction. This has the advantage that the recesses are shaped elongate and thus a disturbed flow of oil which does not move parallel to the respective recess can be formed.

In an advantageous embodiment, the housing part is connected, in particular oil-tightly connected, to the transmission cover, wherein the housing part together with the transmission cover confines oil,

wherein recesses regularly spaced from each other are designed on the outer side of the reduction gear cover at least on a region of the reduction gear cover, and the wall thickness is constant in this region,

in particular, recesses which are regularly spaced apart from one another are also provided on the inner side of the gear reducer cover, which recesses are spaced apart from recesses which are regularly spaced apart from one another and are provided on the outer side of the gear reducer cover in such a way that the wall thickness is constant. The advantage of this is that the increased heat capacity enables a rapid diffusion of the heat flow in the housing and, in addition, better smoothing of the temperature peaks.

In an advantageous embodiment, reinforcing ribs are formed on the inner side of the retarder cover, which ribs cross one another,

in particular, corresponding recesses and elevations are formed between the reinforcing ribs. This has the advantage that the oil flowing past the reinforcing ribs flows turbulently.

In an advantageous embodiment, the wall thickness of the retarder cover periodically fluctuates along a first of the stiffening ribs, in particular along the direction of maximum extension of the first stiffening rib,

the inner side of the first reinforcing rib is designed to be smooth, in particular flat. The advantage is that the stiffening ribs have a high heat capacity and thus enable the diffusion of the heat flow.

In an advantageous embodiment, 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 the first of the stiffening ribs of the retarder 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.

In an advantageous embodiment, the geared motor has a reduction gear, a motor and an adapter flange, in particular an adapter flange arranged between the reduction gear and the motor,

wherein the adapter flange has an annular base body which is rotationally symmetrically formed about the rotational axis of the input shaft of the gear unit and on which an axial projection is formed,

wherein the axial projection is arranged on the side of the adapter flange facing away from the electric machine,

wherein the radial distance area (or radial length range) covered by the housing part overlaps the radial distance area covered by the axial projection in a circumferential angular area not covered by the axial projection,

wherein the area covered by the housing part in the axial direction overlaps the area covered by the axial projection in the axial direction, in particular in the circumferential corner area not covered by the axial projection and in the radial distance area covered by the axial projection,

overlapping the radial distance area covered by the axial projection,

in particular wherein the axial direction is parallel to the axis of rotation of the input shaft, the radial distance is a distance with respect to the axis of rotation of the input shaft, and/or the circumferential direction relates to this axis of rotation of the input shaft,

or wherein the axial projection is designed to be interrupted in the circumferential direction, the housing part projecting into the region of the interruption.

The advantage of this is that the axial projection, on the one hand, is designed to be suitable for a centered connection with the motor and the gear unit, but on the other hand is designed to be as compact as possible. Since centering also requires at least a cylindrical, finished surface on which the orientation is carried out. According to the invention, however, the cylindrical surface is interrupted in the circumferential direction, i.e. is not completely circumferentially designed. The interrupted region can therefore be used by a subregion of the housing part which surrounds the largest toothed part of the gear unit, i.e. the gear wheel which is connected to the output shaft in a rotationally fixed manner, in such a way as to form a housing.

Preferably, the interrupted circumferential angular region is less than 180 °.

Another advantage of the invention is that the type of flange connection of the adapter flange to the electric machine, i.e. the circular flange, is different from the type of flange connection in the direction of the reduction gear, e.g. the square flange. The hole pattern can also be used in different ways accordingly. For example, a rectangular hole pattern can be used for the reduction gear, while a polygonal, i.e. more circular, hole pattern can be used for the electric machine.

In this case, even the radial distance region covered by the holes of the hole pattern facing the electric machine can overlap the radial distance region covered by the holes of the hole pattern facing the gear unit. However, in the circumferential direction, all the holes of the two hole patterns are spaced apart from each other. The holes of the two hole patterns are preferably designed to penetrate the adapter flange.

In particular, the first hole pattern used toward the reduction gear is arranged only in the circumferential corner region covered by the axial projection. In particular the second hole pattern used towards the motor also overlaps the circumferential angular area covered by the interruption zone of the axial projection. Thus, the symmetry axes of the discrete rotational symmetries of the two hole patterns are not coincident but spaced apart from each other. In this way, the adapter flange can be designed particularly compact. Because of the spacing of the symmetry axes, an interrupted region between the annular base body of the adapter flange and the housing part of the gear unit can only be provided.

In an advantageous embodiment, the adapter flange is connected to the circular flange toward the electric machine and to the rectangular or square flange toward the reduction gear. This has the advantage that different flange types with correspondingly different hole patterns and centering surfaces can be provided.

In an advantageous embodiment, the adapter flange has, on its side facing the electric machine, an axially oriented first bore through which a connecting element, such as a threaded rod or a threaded bolt, projects, the connecting element also projecting through the support flange of the electric machine,

wherein the hole pattern of the first bore has a discrete rotational symmetry, in particular a rotational symmetry higher than six-fold, based on the rotational axis of the input shaft. The advantage of this is that the axis of rotation of the rotor shaft of the electric machine is oriented centrally, in particular centrally, with respect to the adapter flange. A stable fastening of the adapter flange can thus be achieved.

In an advantageous embodiment, the adapter flange has, on its side facing the gear unit, an axially oriented second bore which extends through the axial projection of the adapter flange and the annular ring body of the adapter flange,

wherein a connecting element, such as a screw or bolt, protrudes through the second bore and is screwed into a threaded bore formed in the housing part,

in particular, the hole pattern of the second borehole has a discrete rotational symmetry, in particular a two-fold rotational symmetry, on the basis of an axis of symmetry parallel to the axis of rotation of the input shaft, spaced apart from the axis of rotation. The advantage of this is that the geared motor can be designed compactly, since the mechanical gear-side interface, in particular the centering device and the fastening device, is moved and arranged in such a way that an interrupted region of the axial projection can be provided and can be filled at least partially by the accommodation of the toothed part connected to the output shaft.

In an advantageous embodiment, the adapter flange is centered on the receiving part of the reduction gear, in particular, the adapter flange is oriented and centered on the receiving part of the reduction gear coaxially to the axis of rotation of the input shaft,

wherein the receiving part is oriented, in particular centered, on the housing part of the gear unit, in particular by means of a cylindrical centering collar,

in particular, wherein the receiving part is connected to the housing part by means of a bolt,

in particular, the receiving part is held pressed against the housing part by a bolt head of a bolt screwed into an axially oriented threaded hole of the housing part. The advantage of this 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 gear unit, but a receiving part which receives the bearing arrangement, is used for centering. The electric machine is therefore centered on the adapter flange with its support flange facing the adapter flange, which in turn is centered on a receiving part in which the bearing of the input shaft is centrally received. In this way, the electric machine, in particular its rotor shaft, which is supported by bearings received in the support flange, is oriented coaxially with the input shaft of the gear unit.

In an advantageous embodiment, a bearing is accommodated in the receiving part, the inner rings of which are each mounted on the input shaft.

In an advantageous embodiment, the annular ring body is designed completely circumferentially in the circumferential direction, in particular is formed without interruption. Its advantage is high stability. Furthermore, a rotationally symmetrical hole pattern can be provided completely towards the motor, so that the motor can still be fixed in the region of the interruption. The gear unit can also be fixed without interruption, since the hole pattern can be arranged in the axial projection and thus a stable connection can be established between the adapter flange and the housing part of the gear unit.

In one advantageous embodiment, the maximum of the radial distance region covered by the axial projection has four local maxima in dependence on the circumferential angle,

in particular wherein each circumferential angle region covered by a second aperture comprises a circumferential angle corresponding to a respective local maximum. This has the advantage that the holes of the hole pattern facing the reduction gear are arranged in the radially wider region of the axial projection.

In an advantageous embodiment, the axial projection has a finished face facing the reduction gear, the minimum radial distance of which is constant in the sub-region of the circumferential corner region covered by the axial projection,

in particular wherein the sub-region covers more than 80% of the circumferential angular region covered by the axial projection. This has the advantage that accurate centering can be achieved.

In an advantageous embodiment, the cover part is connected to the receiving part, in particular sealingly connected by means of an interposed seal, in particular a flat seal,

in this case, a shaft sealing ring is received in the cover part, which seals against the input shaft, in particular the sealing lip of the shaft sealing ring operating on a sealing surface which is designed on the input shaft. The advantage of this is that the input region, in particular the bearing structure of the input shaft, is sealed in an oil-tight manner. Furthermore, the shaft seal ring further improving the sealing is activated by attaching and connecting the cover parts. The cover part has a centering collar with which the cover part can be aligned on the receiving part. In this way, the shaft sealing ring received in the cover part is centered coaxially with the input shaft of the gear unit, although the bearing is received in the receiving part and therefore the machining of the bearing block during manufacture can be carried out in a single operation by means of a machine tool.

In an advantageous embodiment, the clamping ring and the clamping ring are mounted on the input shaft, wherein the clamping ring bears against a first of the bearings,

wherein the clamping ring is connected with the input shaft in a force-locking/friction-locking manner,

in particular, the axially aligned screw is supported on the clamping ring and screwed into an axially aligned threaded bore of the clamping ring, so that the screw supported on the clamping ring presses the clamping 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 contact pressure.

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

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

in particular, the bevel pinion is restrained in the axial direction by a washer which is held in a form-fitting manner by a screw which is screwed into the input shaft. The advantage of this is that the input bevel gear stage is followed by the spur gear stage. The gears of the spur gear stage can be designed to be in helical engagement. Thus enabling low noise operation.

Further advantages are given by the dependent claims. The invention is not limited to the combination of features of the claims. The individual features of the claims and/or other possible combinations of features of the description and/or the drawings can be derived by the person skilled in the art, in particular from the technical problems stated and/or the technical problems stated in comparison with the prior art.

Drawings

The invention will now be described in detail with reference to the schematic drawings:

fig. 1 shows a gear unit with an adapter flange 3 for connection to an electric motor 120 in an oblique view.

Fig. 2 shows the gear unit from another viewing direction.

The gear unit is shown in fig. 3 in a section.

Fig. 4 shows a further sectional view of the gear unit.

Fig. 5 shows a section of the gear unit perpendicular thereto.

Fig. 6 shows a plan view of the gear unit with the adapter flange 3, corresponding to fig. 1.

Fig. 7 shows a perspective view of a reduction gear with an exploded adapter flange 3.

Fig. 8 shows the adapter flange 3 in an oblique view from a first viewing direction.

Fig. 9 shows the adapter flange 3 in an oblique view from a second viewing direction.

Fig. 10 shows a sectional view of the gear unit such that the input region of the gear unit is visible.

Fig. 11 shows the shaft, the toothed element and the bearing of the gear unit in an oblique view, with the housing part 1 of the gear unit and the lubricating oil of the gear unit omitted.

Fig. 12 shows a reduction gear connected to the motor 120 in an oblique view.

Detailed Description

As shown in the drawing, an adapter flange 3 is arranged between the electric motor 120 and the housing part 1 of the gear unit, so that the electric motor 120 can be centered on the adapter flange and can be mounted on the adapter flange 3 by means of screws.

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

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

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

The radial distance is always based on the axis of rotation 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 axis of rotation of the input shaft 4.

The adapter flange 3 has, on its side facing the gear housing 1, an axial projection 90 projecting in the axial direction towards the housing part 1, but interrupted in the circumferential direction by a wall region 92 that is thinned. In this case, the thinned wall region 92 has a smaller extent, in particular a smaller wall thickness, in the axial direction than in the circumferential corner region covered by the axial projection 90.

That is to say, the adapter flange 3 preferably has an annular base body which is designed rotationally symmetrically with respect to the rotational axis of the input shaft 4 of the gear unit and on which the axial projection 90 is formed on the gear unit side, but which is not rotationally symmetrical but is interrupted in a circumferential angular region. The housing part 1, in particular the bulge of the housing part 1, which at least partially surrounds the output gear 113 in a housing-forming manner, projects into this interrupted circumferential angle region, wherein the radial distance region covered by the housing part 1 in this interrupted region, that is to say in this circumferential angle region and in the region covered by the basic body in the axial direction, overlaps with the radial distance region covered by the basic body.

The housing part 1 therefore projects into the interrupted region of the axial projection 90.

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

Thus, the bolts for connecting the housing part 1 to the adapter flange 3 are arranged in a rectangular arrangement.

That is, a square flange may be used toward the reducer, and a circular flange may be used toward the motor 120.

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

The circumferential angle regions covered by the respective holes 91 each contain a circumferential angle value of each maximum value.

Accordingly, the respective eyelets 91 are each arranged in a radially expanded region of the axial projection 90.

The axial projection 90 has an inner cylindrical surface region on its inner circumference, that is to say at its smallest radial distance, which surface region is however interrupted in the circumferential corner region not covered by the axial projection 90.

This inner peripheral portion serves as a centering receptacle for the receiving part 41 of the reduction gear. The inner cylindrical surface area is oriented coaxially with the axis of rotation of the input shaft 4.

Furthermore, the axial projection has a finished, axially projecting torus in the circumferential angular region covered by the axial projection 90.

By means of this annular surface, the adapter flange 3 rests on the finished flat surface region of the housing part 1. In this case, a respective axially oriented hole, in particular a threaded hole, is formed in each of the finished flat surface regions, wherein a screw is inserted through the bore 91 and screwed into the threaded hole 71 formed in the finished flat surface region of the housing part 1.

The torus and the surface area of the axial projection 90, in which the hole 91 is formed, are located at the same axial position. This axial position is the position furthest from the motor 120, covered by the adaptor flange 3.

The thinned wall region 92 of the adapter flange 3 lies on the bulge, in particular the elevation, of the housing part 1 or at least has only a small distance. The crowning at least partially surrounds the gear wheel 113 connected to the output shaft in such a way that it forms a housing.

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

The gear wheel 113 connected in a rotationally fixed manner to the output shaft 5 together with the crowning covers a region in the axial direction, that is to say in a direction perpendicular to the axis of rotation of the input shaft, which region comprises the region covered by the bearing 47 of the input shaft 4.

The electric machine 120 has a stator housing which is axially connected on both sides to a respective support flange in the form of a circular flange. Each of the two support flanges receives a respective bearing, which is mounted on the rotor shaft of the electric machine 120. The rotor shaft is thus rotatably supported by two bearings received in the support flange.

The two supporting flanges are designed as circular flanges. Thus, they have a substantially circular outer peripheral portion. The hole pattern of the connecting bolts for connecting the first of the two support flanges to the adapter flange 3 has a discrete rotational symmetry, wherein the rotational symmetry axis corresponds to the rotational axis of the rotor shaft, in particular, that of the input shaft 4 arranged coaxially to the rotor shaft. The first support flange of the adapter flange 3 facing the motor 120 likewise has a hole pattern with such a discrete rotational symmetry.

The bearing 47 is received in a receiving part 41, which has a radially outwardly projecting, circumferentially encircling flange that is pressed onto the housing part 1 by means of a screw that is screwed into an axially oriented threaded bore of the housing part 1.

Here, a step is finished on this flange and is therefore designed to be suitable for centering on the housing part 1.

The bearing 47 is fitted onto the input shaft 4, which is thus rotatably supported.

The cover part 46 is pressed onto the receiving part 47 by means of bolts screwed into threaded holes of the receiving part 47, in particular by means of the bolt heads of these bolts. A shaft seal ring 45 that seals the cover member 46 toward the input shaft 4 is received in the cover member 46.

A clamping ring 52 and a clamping ring 50 which bear against a first one of the bearings 47 are fitted on the input shaft 4, the clamping ring 50 being connected to the input shaft 4 in a force-fitting manner. Axially oriented bolts 51 are supported on the clamping ring 50 and are screwed into axially oriented threaded bores of the clamping ring 52, so that the bolts supported on the clamping ring 50 press the clamping ring 52 against the first bearing 47. In particular, the clamping ring 52 is pressed onto the inner ring of the first bearing 47.

The input shaft 4 penetrates the cover member 46. The input shaft 4 is connected in a rotationally fixed manner to a bevel pinion 49, the toothing of which meshes with the toothing of the gearwheel 48, in particular of a bevel gearwheel.

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

The bevel pinion 49 is slipped onto the conical end region of the input shaft 4 and is fixed axially by means of a washer, which is pressed onto the end face of the input shaft 4 by a bolt screwed centrally into the end face of the input shaft 4. Furthermore, the bevel pinions 49 are connected in a force-fitting manner and/or in a form-fitting manner, in particular by means of a key connection.

An axially projecting, circumferentially encircling centering collar is formed on the cover part 46, which is aligned and centered on a centering seat formed on the receiving part 41.

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

The gear 48 is connected in a rotationally fixed manner to an intermediate shaft 111 which is mounted rotatably by means of bearings received in the housing parts and is connected in a rotationally fixed manner to a toothed segment 112 which meshes with a toothed segment of a gear 113 which is connected in a rotationally fixed manner to the output shaft 5.

The gear unit according to the invention, which is preferably a two-stage gear unit, therefore has an input bevel gear stage, which is followed by a spur gear stage arranged on the output side. The teeth of the spur gear stages preferably each have an angle of inclination which is different from zero.

The intermediate shaft 111 is connected to 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, the intermediate shaft 111 rotates at least faster than the output shaft 5.

The oil level of the oil in the interior of the gear unit covers or reaches the pinion toothing. However, the two bearings 47 of the input shaft 4 are arranged above the oil level and are therefore not lubricated after a long stop of the retarder.

Therefore, once the speed reducer is operated, the shaft-end pump 100 driven by the intermediate shaft 111 pumps the oil from the oil sump disposed 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 either.

The input shaft 4 is parallel to the normal direction of the oil sump surface, especially when the retarder is stopped for a long time.

The other bearings, toothed sections (112, 49) and gears (48, 113) are always at least partially immersed in the oil sump of the gear unit.

As shown in fig. 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, designed as a blind bore, and is closed off at its end facing the electric machine 120 by a closure plug 105.

The 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 through the receiving part 41, which is closed off toward the input shaft 4 by a plug 107, which is not, however, completely sealed, but allows a small amount of oil to pass through, which then reaches the lower bearing 47 in the gap between the housing part 1 and the input shaft 4, i.e., at a greater distance from the electric machine 120.

The axially oriented blind hole 106 formed in the receiving part 41 from the outside opens into a radial hole 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 feeds the upper bearing 47, i.e. facing the electric motor 120. Consequently, the second bearing 47 arranged below the first bearing 47 is also fed subsequently.

The two bearings 47 are preferably designed as radial thrust bearings.

The receiving part 41, which is connected in an oil-tight manner to the housing part 1, together with the cover part 46, which is connected in an oil-tight manner to the receiving part 41, enclose the interior space region of the gear unit.

During the operation of the gear unit and thus during the rotational movement of the intermediate shaft 111, oil is supplied by the shaft end pump 100 counter to the direction of gravity and thus lubricates the bearing 47 with oil. In addition, the oil flowing past the bearings 47 absorbs the heat loss, which is then dissipated from the oil sump to the surroundings.

In order to achieve the lowest possible heat transfer resistance from the oil sump to the surroundings or at least to the housing part 1, the inner side of the housing part 1 is provided with regions having recesses 30, which are in particular regularly spaced apart from one another.

In these regions, the wall thickness is preferably not constant, but rather these regions are designed smoothly, in particular flatly, on their outer sides.

Thus, the wall thickness varies in these regions in synchronism with the recesses 30.

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

Preferably, the recesses 30 are arranged below the oil level and thus provide an increased surface 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 regions arranged between the recesses 30, in particular thickened by the flat structure of the respective regions on the outside, in particular due to the greater heat capacity produced by the thickened portions. From there, the heat is then dissipated in the housing part 1 and conducted away to the surroundings.

In other regions, in which the wall thickness is constant, recesses 2 are provided on the outside of the housing part. Thus, 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.

Here, too, each of the recesses 2 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.

Thus, the recess 2 can be formed on the housing part 1 in order to achieve a particular design impression which indicates the origin. In contrast, the recess 30 formed only on the inner side is not used for the design impression, but is used for improving heat dissipation.

On the lower side of the retarder, the inner space of the retarder is closed by means of a retarder cover 31, which likewise has a recess 2 and a constant wall thickness, but in which reinforcing ribs 32 are formed on the inner side of the retarder cover, which ribs intersect one another. The retarder cover 31 is therefore on the one hand rigid and also conveys a design impression indicating the origin, wherein the underside of the oil sump is thus stabilized, since the flowing oil must not only overcome the reinforcing ribs 32 but also the recesses and elevations between the reinforcing ribs 32. Thus, as the oil moves, less laminar flow, more disturbed flow, is formed in the oil sump. Thereby also improving the heat transfer from the oil to the reducer cover 31.

Arranged in the receiving part 41 is a radial bore 43 which extends through the receiving part 41 at a distance from the radial bore 108 in the circumferential direction and into which opens an axially oriented blind bore formed in the receiving part which projects out of the receiving part 41 toward the oil sump. Thus, it is possible to drain oil from the spatial region between the input shaft and the receiving part. In particular in the case of an overpressure in this region, this oil is discharged for pressure relief.

The radial bores 43 are closed radially to the outside by the housing part 1 into which the receiving part 41 projects. The receiving part 41 has another such relief, mirror-symmetrically with respect to a plane of symmetry containing the rotational axis of the input shaft.

That is, the receiving part 41 has in this way four radial bores through the receiving part spaced apart from one another in the circumferential direction at the same axial position.

In a further embodiment according to the invention, the bevel pinion 49 is designed in one piece, in particular integrally, with the input shaft.

List of reference numerals:

1 housing part

2 concave part

3 adapting flange

4 input shaft

5 output shaft

30 recess

31 speed reducer cover

32 reinforcing rib

40 shaft seal ring

41 receiving part

42 bolt

43 radial hole

44 axial bore

45 shaft seal ring

46 cover part

47 bearing, in particular tapered roller bearing

48-gear, in particular bevel gear

49 bevel pinion

50 clamping ring

51 bolt

52 compression ring

60 bolt

61 first eyelet

71 hole, especially threaded hole

90 axial projection

91 second eyelet

92 thinned wall region

100 shaft end pump

101 radial hole

102 axial hole

103 radial hole

104 closure plug

105 closing plug

106 axial hole

107 plug

108 radial holes

111 intermediate shaft

112 tooth part

113 Gear

120 motor.

Claims

1. A geared motor comprising a gear unit having an input shaft and a housing with a housing part, a receiving part and a cover part, and in particular a gear unit cover, wherein the housing at least partially encloses a toothed part and an oil in such a way that it forms a housing,

the input shaft is rotatably supported by two bearings received in the receiving part, in particular wherein the inner rings of the two bearings are slipped over the input shaft,

2. The reduction motor in accordance with claim 1,

it is characterized in that the preparation method is characterized in that,

a third channel is arranged in the housing part, which third channel is designed mirror-symmetrically to the first channel, in particular with respect to a mirror plane containing the rotational axis of the input shaft.

3. Gearmotor according to one of the preceding claims,

it is characterized in that the preparation method is characterized in that,

a fourth channel is arranged in the receiving part, which fourth channel is designed mirror-symmetrically to the second channel, in particular with respect to a mirror plane containing the rotational axis of the input shaft.

4. Gearmotor according to one of the preceding claims,

it is characterized in that the preparation method is characterized in that,

the first channel has a radially oriented first blind hole formed in the housing part, which opens into an axially oriented second blind hole formed in the housing part and closed off from the surroundings by means of a closing plug, which second blind hole intersects a radially oriented third bore running through the housing part, which third bore opens into a radially oriented fourth bore formed in the receiving part, which fourth bore intersects an axially oriented fifth blind hole formed in the receiving part,

in particular, wherein the first channel has an outlet located above the bearing of the input shaft,

in particular wherein the first channel comprises a first hole, a second hole, a third hole, a fourth hole and a fifth hole,

in particular, the receiving part has four radial bores which are spaced apart from one another in the circumferential direction and which extend through the receiving part and are arranged at the same axial location.

5. Gearmotor according to one of the preceding claims,

it is characterized in that the preparation method is characterized in that,

the fourth bore is only incompletely closed off 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 passes from the fourth bore, alongside the plug, flows out in the axial direction between the bearings of the input shaft, and supplies the bearing, out of the two bearings of the input shaft, which is arranged below the fourth bore, with oil.

6. Gearmotor according to one of the preceding claims,

it is characterized in that the preparation method is characterized in that,

the input shaft is connected in a rotationally fixed manner to a bevel pinion which meshes with a gear, in particular a bevel gear, which is connected in a rotationally fixed manner to the intermediate shaft,

in particular, the bevel pinion is restrained in the axial direction by a washer which is held in a form-fitting manner by a screw which is screwed into the input shaft.

7. Gearmotor according to one of the preceding claims,

it is characterized in that the preparation method is characterized in that,

8. Gearmotor according to one of the preceding claims,

it is characterized in that the preparation method is characterized in that,

each of the recesses extends longer in a direction perpendicular to the axial direction, i.e. perpendicular to the rotational axis of the input shaft, than in the axial direction.

9. Gearmotor according to one of the preceding claims,

it is characterized in that the preparation method is characterized in that,

the one or more regions are arranged below the oil level of the oil, in particular below the oil level that occurs when the retarder is shut down,

and/or

Recesses regularly spaced apart from one another are formed on the outer side of the housing part in the second region and the wall thickness is constant in the second region,

in particular, recesses which are regularly spaced apart from one another are also formed on the inner side of the housing part, which recesses are spaced apart from recesses which are regularly spaced apart from one another and are formed on the outer side of the housing part in such a way that the wall thickness is constant.

10. Gearmotor according to one of the preceding claims,

it is characterized in that the preparation method is characterized in that,

in the second region, each of the recesses 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.

11. Gearmotor according to one of the preceding claims,

it is characterized in that the preparation method is characterized in that,

the housing part is connected, in particular oil-tightly, to the gearbox cover, wherein the housing part together with the gearbox cover confines oil,

in particular, recesses which are regularly spaced apart from one another are also provided on the inner side of the gear reducer cover, which recesses are spaced apart from recesses which are regularly spaced apart from one another and are provided on the outer side of the gear reducer cover in such a way that the wall thickness is constant.

12. Gearmotor according to one of the preceding claims,

it is characterized in that the preparation method is characterized in that,

reinforcing ribs are formed on the inner side of the reducer cover, the reinforcing ribs crossing each other,

in particular, corresponding recesses and elevations are formed between the ribs,

and/or

The wall thickness of the reducer cover periodically fluctuates along a first of the stiffening ribs, in particular along the direction of maximum extension of the first stiffening rib,

wherein the inner side of the first reinforcing rib is designed to be smooth, in particular flat,

and/or

The period length of the space of the variation curve of the wall thickness in the first region of the housing part is equal to the period length of the space of the variation curve of the wall thickness in the second region and/or equal to the period length of the space of the variation curve of the wall thickness along the first of the stiffening ribs of the retarder cover.

13. Gearmotor according to one of the preceding claims,

it is characterized in that the preparation method is characterized in that,

the gear motor has a reduction gear, a motor and an adapter flange, in particular an adapter flange arranged between the reduction gear and the motor,

wherein the radial distance area covered by the housing part overlaps the radial distance area covered by the axial projection in a circumferential angular area not covered by the axial projection,

overlapping the radial distance area covered by the axial projection,

14. Gearmotor according to one of the preceding claims,

it is characterized in that the preparation method is characterized in that,

the adapting flange is connected with the round flange towards the motor and is connected with the rectangular flange or the square flange towards the speed reducer,

and/or

The adapter flange has, on its side facing the electric machine, an axially oriented first bore (61) through which a connecting element, such as a screw or bolt, projects, which also projects through the support flange of the electric machine,

wherein the hole pattern of the first bore has a discrete rotational symmetry, in particular a rotational symmetry higher than six-fold, based on the rotational axis of the input shaft,

and/or

The adapter flange has, on its side facing the gear unit, an axially oriented second bore (91) which extends through the axial projection of the adapter flange and the annular ring body of the adapter flange,

wherein a connecting element, such as a screw or a bolt, protrudes through the second bore (91) and is screwed into a threaded hole formed in the housing part,

in particular, the hole pattern of the second bore has a discrete rotational symmetry, in particular a two-fold rotational symmetry, based on parallel symmetry axes spaced apart from the rotational axis of the input shaft.

15. Gearmotor according to one of the preceding claims,

it is characterized in that the preparation method is characterized in that,

the adapter flange is centered on the receiving part of the reduction gear, in particular oriented and centered coaxially to the axis of rotation of the input shaft,

in particular wherein the receiving part is held pressed against the housing part by a bolt head of a bolt screwed into an axially oriented threaded hole of the housing part,

and/or

The receiving part is provided with a bearing, the inner rings of the bearing are respectively sleeved on the input shaft,

and/or

The annular ring body is designed completely circumferentially in the circumferential direction, in particular is formed without interruption,

and/or

The maximum of the radial distance region covered by the axial projection has four local maxima in relation to the circumferential angle,

in particular wherein each circumferential angle region covered by a second aperture (91) comprises a circumferential angle corresponding to a respective local maximum,

and/or

The axial projection has a finished face directed towards 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 particular wherein the sub-region covers more than 80% of the area of the circumferential angle covered by the axial projection,

and/or

The cover part is connected to the receiving part, in particular sealingly connected by means of an interposed seal, in particular a flat seal,

wherein a shaft sealing ring is received in the cover part, which sealing ring seals towards the input shaft, in particular a sealing lip of the shaft sealing ring works on a sealing surface designed on the input shaft,

and/or

A clamping ring (52) and a clamping ring (50) are mounted on the input shaft, wherein the clamping ring (52) rests on a first bearing (47) of the bearings,

wherein the clamping ring (50) is connected to the input shaft (4) in a force-fitting manner,

in particular, axially aligned screws (51) are supported on the clamping ring (50) and are screwed into axially aligned threaded bores of the clamping ring (52), so that the screws supported on the clamping ring (50) press the clamping ring (52) onto the first bearing (47), in particular onto an inner ring of the first bearing (47).