CN212536618U - Speed reducer with shaft and housing part - Google Patents

Abstract

The invention relates to a reduction gear having a shaft and a housing part, wherein a bearing is received in the housing part, the flange part is connected to the housing part, the flange part is sealed off towards the shaft by means of a first labyrinth seal and a second labyrinth seal, the first labyrinth seal is spaced apart from the second labyrinth seal in the axial direction, the shaft has a projection, which is arranged axially, that is to say in the axial direction, between the first labyrinth seal and the second labyrinth seal.

Description

Speed reducer with shaft and housing part

Technical Field

The utility model relates to a reduction gear with axle and housing part.

Background

It is generally known that a gear unit has a shaft which is mounted in a housing part of the gear unit by means of bearings and to which a toothed part is connected.

SUMMERY OF THE UTILITY MODEL

Therefore, the object of the present invention is to provide a speed reducer with high safety against leakage.

In the case of a reduction gear having a shaft and a housing part, an important feature of the invention is that,

in the housing part, a bearing, in particular a bearing for rotatably supporting the shaft,

the flange member is connected to the housing member,

the flange part is sealed towards the shaft by means of a first labyrinth seal and a second labyrinth seal,

the first labyrinth seal is axially spaced from the second labyrinth seal,

the shaft has a projection, in particular a projection running in the circumferential direction,

the projection is arranged axially, that is to say in the axial direction, between the first labyrinth seal and the second labyrinth seal.

The advantage of this is that the shaft can be sealed in a contactless manner and the safety can be increased in order to reduce the risk of leakage to the environment, by virtue of the shaft having a projection which acts as a draining edge (abtrpfkante) in the rest state and as a centrifugal edge during the rotational operation of the shaft. Furthermore, the axis of rotation of the shaft is oriented substantially horizontally. The oil collected in the second spatial region around the projection can be discharged via a return line into the oil sump of the gear unit. High security against leakage can thus be achieved.

In an advantageous embodiment, the first spatial region of the clearance is adjacent to the bearing,

the bearing can be supplied with lubricant from the first spatial region, in particular the rolling elements of the bearing,

the first space region can be supplied with lubricant from a first radial bore of the flange part via a first axial bore running through the housing part, which first axial bore opens into the first radial bore. The advantage of this is that the bearings can be supplied with lubricating oil which can be transported by the oil delivery device from the interior of the gear unit towards the flange part and from there towards the bearings received in the housing parts.

In an advantageous embodiment, a free second spatial region is provided axially between the first labyrinth seal and the second labyrinth seal, which second spatial region is delimited by the flange part, the first labyrinth seal, the second labyrinth seal and the shaft,

the second radial bore of the flange part opens into the second space region, wherein a second axial bore which penetrates the housing part opens into the second radial bore,

the second axial hole opens into the inner space of the reducer,

in particular for returning oil from the second spatial region to the oil sump of the retarder. The advantage is that oil arriving through the labyrinth seal can flow back into the oil sump.

In an advantageous embodiment, the projection is formed on the shaft and the second spatial region is arranged on the shaft in such a way that oil dripping or being thrown off from the projection reaches the second spatial region. This has the advantage that the safety in terms of collection and return of the leakage oil can be improved.

In an advantageous embodiment, the plug seals the first radial bore toward the second spatial region, in particular wherein the first radial bore is sealed toward the environment by a further plug and/or wherein the second radial bore is sealed toward the environment by a third plug. The advantage of this is that simple production is possible by means of the passage of the flange part and nevertheless a high tightness is possible.

In an advantageous embodiment, the projection is arranged axially between two circumferential grooves formed on the shaft, in particular adjacent to the projection. Advantageously, the projection can be made by forming two annular grooves. The projection is produced by machining two spaced apart annular grooves in the cylindrical surface without additional cost.

In an advantageous embodiment, the maximum diameter of the shaft in the region of the shaft adjacent to the first of the annular grooves is equal to the maximum diameter of the shaft in the region covered by the projection in the axial direction. The advantage is that the manufacture can be carried out without special costs by machining two grooves.

In an advantageous embodiment, the maximum diameter of the shaft in the region of the shaft adjoining the second of the annular grooves is equal to the maximum diameter of the shaft in the region covered by the projection in the axial direction. The advantage is that the manufacture can be carried out without special costs by machining two grooves.

In an advantageous embodiment, the maximum diameter of the bearing seat of the inner ring of the bearing is equal to the maximum diameter of the shaft in the region covered by the projection in the axial direction. The advantage is that the manufacture can be carried out without special costs by machining two grooves.

In an advantageous embodiment, the maximum diameter of the bearing seat of the inner ring of the bearing is equal to the maximum diameter of the shaft in the region covered by the projection in the axial direction. The advantage is that the manufacture can be carried out without special costs by machining two grooves.

In an advantageous embodiment, the first radial bore is designed as a stepped bore,

in particular, the plug is arranged in a narrowed region of the first radial bore, which opens into the second space region. The advantage is that a simple manufacture can be achieved.

In an advantageous embodiment, the second radial bore is designed as a stepped bore. The advantage is that a simple manufacture can be achieved.

In an advantageous embodiment, the oil flow conveyed by the oil conveying device flows into the first radial bore. This has the advantage that an active or passive oil supply can be carried out and thus an adequate lubrication of the bearings can be achieved.

In an advantageous embodiment, the oil delivery device has an oil pump driven by the motor or the shaft of the gear unit and/or a collecting unit for collecting oil that is sprayed high in the rotational movement of the toothed part of the gear unit, in particular against the direction of gravity. The advantage of this is that in the electric motor, lubrication of the bearings can be carried out even in the idle state of the gear unit, i.e. before starting, and that no motor for the pump is required when using an oil pump driven by the shaft, in particular a shaft end pump.

In an advantageous embodiment, the bearing is a radial thrust bearing, and/or the shaft is designed as a hollow shaft,

in particular wherein the shaft is the output shaft of the reducer, wherein the shaft is the largest diameter of all the shafts of the reducer. This has the advantage that high transverse forces introduced on the load side can be absorbed.

In an advantageous embodiment, the flange part is formed integrally, in particular in one piece,

in particular

The flange part together with the first labyrinth seal and/or the second labyrinth seal is produced from plastic as a plastic injection-molded part,

or wherein the flange part and the first labyrinth seal and/or the second labyrinth seal are made of metal,

or wherein the flange part and the first labyrinth seal and/or the second labyrinth seal are designed as additively manufactured components in which the first radial bore and the second radial bore are designed as shaped or additively formed channels, in particular, that is, not manufactured by means of an open-pored manner. The advantage is that a simple manufacture can be achieved.

In an advantageous embodiment, a sealing ring, in particular a V-ring,

in particular, the sealing ring is connected in a rotationally fixed manner, in particular in a force-fitting manner, to the shaft, and the sealing lip of the sealing ring extends over or seals against a finished, flat sealing surface formed on the flange part, wherein the normal of the plane containing the sealing surface is parallel to the axial direction. This has the advantage that a dust-proof device as well as an additional seal can be provided. The working surface is not on the shaft but on the flange part. The finished, in particular ground, surface of the flange part is sufficient.

In an advantageous embodiment, on the side of the flange part facing away from the bearing, a cover plate is connected to the flange part,

wherein the radial length region covered by the cover plate includes the radial length region covered by the seal ring, except for the gap between the cover plate and the shaft,

in particular wherein the sealing lip of the sealing ring contacts the finished surface of the flange part and/or wherein the cover plate is spaced from the shaft. This has the advantage that additional protection is provided. In particular, the V-shaped ring can be protected in that it is radially enclosed by the cover plate and only a small gap between the cover plate and the shaft is free. But since the seal ring is directly mounted on the shaft and thus there is no gap between the seal ring and the shaft, the sealability is improved in the axial direction. The sealing ring uses a running surface formed on the flange part, but oriented perpendicular to the surface of the shaft, that is to say perpendicular to the direction of the axis of rotation of the shaft.

In an advantageous embodiment, the oil flow conveyed by the oil conveying device flows into the first radial bore. The advantage of this is that the oil flow is conveyed by an active and/or passive oil conveying device, i.e. potential energy is conveyed to the oil in the gravitational field and subsequently the oil flows past the shaft sealing ring or the bearing, while the conveyed potential energy is reduced. The shaft seal ring and the bearing can be supplied with lubricating oil.

In an advantageous embodiment, the oil delivery device has an oil pump driven by the electric motor or the shaft of the gear unit and/or a collecting unit for collecting oil that is sprayed high during the rotational movement of the toothed part of the gear unit, in particular that is sprayed counter to the direction of gravitational force. The advantage of this is that the oil already lubricates the bearings before the start of the rotational movement of the shaft when the electric motor is used and that no separate and/or additional energy supply for the electric motor of the oil pump is required when the oil pump is designed as a shaft-end pump.

In an advantageous embodiment, the axial bore through the housing part opens into the first radial bore, in particular so that lubricating oil of the gear unit can be supplied to the first radial bore. This has the advantage that the oil supply can be established simply.

In an advantageous embodiment, the bearing is a radial thrust bearing, and/or the shaft is designed as a hollow shaft,

in particular wherein the shaft is the output shaft of the reducer, wherein the shaft is the largest diameter of all the shafts of the reducer. The advantage is that the load driven by the shaft can introduce lateral forces, which can be absorbed by the bearings.

In an advantageous embodiment, the flange part is formed integrally, in particular in one piece,

in particular

The flange part and the sealing ring are made as plastic injection-molded parts from plastic,

-or wherein the flange part and the sealing ring are made of metal,

or wherein the flange part and the sealing ring are designed as an additively manufactured component in which the first radial bore and the second radial bore are designed as molded or additively formed channels, in particular, that is to say are not manufactured by means of an open-pored manner.

This has the advantage that simple manufacture and improved tightness can be achieved. In the case of a design made of plastic, a very cost-effective production can be achieved. In the case of designs made of metal, it is important that there is a sufficiently large gap in the labyrinth seal so that the shafts do not come into contact when lateral forces occur. In an additive embodiment, the flange part and the sealing ring can be made of metal, in particular aluminum, or of plastic.

In an advantageous embodiment, the second radial bore of the flange part opens into a second axial bore which extends through the housing part and opens into the interior of the gear unit. This has the advantage that the oil supplied can flow back into the oil sump of the gear unit after the supply of the bearing or shaft sealing ring. The cooled oil or the oil sprayed to a high point by means of the oil transfer device is conveyed from the oil sump or the subsequent oil transfer device to the first radial bore and from there subsequently to the bearing or the shaft sealing ring.

In an advantageous embodiment, the cover plate is connected to the flange part,

the cover plate is arranged on the side of the sealing ring, in particular the V-ring, facing away from the bearing in the axial direction. Its advantage is that the dust-proof function of shaft sealing ring can be realized. Only a narrow gap remains between the cover plate and the shaft. Furthermore, the leakage oil must not only pass over the two labyrinth seals and the projection arranged in the middle, but also over the sealing region of the sealing ring.

In an advantageous embodiment, the radial length region covered by the cover plate comprises the radial length region covered by the sealing ring, which, in addition to the radial length region covered by the sealing lip of the shaft sealing ring,

in particular, the sealing lip of the shaft sealing ring contacts the finished running surface of the shaft, wherein the cover plate is spaced apart from the shaft. Advantageously, the cover covers the shaft sealing ring except for a narrow gap region towards the shaft.

In an advantageous embodiment, the sealing ring is made of plastic and/or rubber. This has the advantage that simple production is possible and that materials with a low thermal load capacity can be used as the oil is cooled.

In an advantageous embodiment, the sealing ring is in full contact with the flange part in the circumferential direction, except for the circumferential angular region covered by the first and second channels. This has the advantage that the second space region can be made highly sealed with respect to the first space region having a higher temperature level.

In an advantageous embodiment, the radial length region covered by the sealing ring comprises the radial length region covered by the shaft sealing ring. This has the advantage that the sealing ring and the shaft sealing ring are arranged on the same diameter.

In an advantageous embodiment, the radial length region covered by the sealing ring overlaps the radial length region covered by the shaft sealing ring. The advantage is that the sealing ring shields the second spatial region sufficiently from the first spatial region.

In an advantageous embodiment, the first radial bore is sealed off from the surroundings by means of a plug which is at least partially inserted into the first radial bore. The advantage is that a simple manufacture can be achieved.

In an advantageous embodiment, the second radial bore is sealed off from the surroundings by means of a plug which is at least partially inserted into the second radial bore. The advantage is that a simple manufacture can be achieved.

Other possible combinations of the features of the description and/or of the drawings may be obtained by the person skilled in the art, especially from the objects set forth and/or by comparison with the prior art.

Drawings

The invention is described in detail below with reference to the schematic drawings:

fig. 1 shows a sectional view of a gear unit according to the invention with a bearing arrangement.

Fig. 2 shows an enlarged detail of fig. 1.

List of reference numerals:

1 housing part

2 Flange part

3 first radial hole

4 plug

5V-shaped ring

6 shaft

7 second spatial region

8 first axial hole

9 bearing

10 channel

11 second labyrinth seal

12 second radial hole

13 second axial hole

14 first spatial region

15 first annular groove

16 convex part

17 first labyrinth seal

18 second annular groove

Detailed Description

As shown in the drawing, the shaft 6, in particular a hollow shaft, is rotatably mounted by means of a bearing 9, in particular a radial thrust bearing, wherein the bearing 9 is accommodated in the housing part 1 of the gear unit.

The reducer has a further shaft connected in a rotationally fixed manner to a toothed member, the toothing of which meshes with the toothing of a further toothed member connected in a rotationally fixed manner to the shaft 6.

The housing of the gear unit is formed by the housing part 1 and the further housing part.

In the inner space enclosed by the housing there are the toothed parts and the lubricating oil. The inner space is only partially filled with lubricating oil, so that in the rest state an oil level is present in the inner space which does not reach or only partially reaches the rolling bodies of the bearing 9, in particular only reaches the innermost-lying rolling bodies of the bearing 9.

The reduction gear therefore has an active and/or passive oil supply, with which, at least during operation of the reduction gear, all of the rolling bodies of the bearing 9, that is to say those which are disposed at the highest point, are supplied with lubricating oil from the oil sump, that is to say those which are located below the oil level.

Furthermore, the housing part 1 has a first axial bore 8 through which the supplied lubricant is conducted to a first radial bore 3, which is arranged in the flange part 2, which covers the bearing 9 towards the surroundings.

The flange part 2 is connected to the housing part 1 in a sealing manner by means of screws and a flat seal arranged in the middle.

The first radial bore 3 opens into an annular, free first spatial region 14, which adjoins the bearing 9, in particular the rolling elements of the bearing 9. The bearing 9 can thus be lubricated with lubricating oil via the first radial bore 3 and the annular, free first spatial region 14.

The free first spatial region 14 is directly axially adjacent to the bearing 9 and covers at least the free space which is present in the radial direction between the inner ring and the outer ring of the bearing 9. The area covered by the first spatial area in the axial direction therefore directly adjoins the axial area covered by the bearing 9. The radial length area covered by the first spatial area 14 is comprised by the radial length area covered by the bearing. Since the inner ring of the bearing 9 rests in a further embodiment on a fastening ring arranged on the shaft 6 or in the embodiment shown in fig. 1 on a step of the shaft 6. The outer ring is likewise axially limited by the flange part 2 itself, either by means of a ring part or by the embodiment according to fig. 1.

The radial spacing is referred to in relation to the axis of rotation of the shaft 6, with the axial direction being parallel to the direction of the axis of rotation of the shaft 6.

The shaft 6 is preferably designed as an output shaft.

The shaft 6 is sealed in a contactless manner toward the flange part 2 by means of a first labyrinth seal 17 and a second labyrinth seal 11 spaced axially apart therefrom. Two labyrinth seals are received or formed on the flange part 2, in particular by corresponding circumferential annular grooves.

A second spatial region 7 is arranged axially between the two labyrinth seals. The second spatial region 7 is likewise annular. The plug 4 separates the second spatial region 7 from the first radial bore 3.

Axially between the first labyrinth seal 17 and the second labyrinth seal 11, the shaft 6 has a first annular groove 15 and a second annular groove 18 spaced axially apart from the first annular groove, wherein axially between the two annular grooves a projection 16 is provided which completely surrounds in the circumferential direction. The largest outer diameter of the projection 16 corresponds to the outer diameter of the shaft 6 in the region of the first labyrinth seal 17 and the outer diameter of the shaft 6 in the region of the second labyrinth seal 11.

Since the first annular groove 15 and the second annular groove 18 are therefore cut radially deeper, oil that may enter the annular grooves, in particular leakage oil, is driven by the centrifugal force caused in the rotational movement of the shaft 6 towards the projection 16 and is subsequently thrown away. In the shut-down state, the projection 16 serves as a draining edge for this oil. The oil escaping from the projection 16 is anyway collected in the second spatial region 7 and from there conveyed to the return. As a return, the second spatial region 7 opens in its lower end region in the direction of attraction into a second radial bore 12 of the flange part 2, which is sealed off toward the surroundings by means of a further plug and opens into a second axial bore 13 running through the housing part 1, which in turn opens into the interior spatial region of the gear unit and thus returns the oil to the oil sump of the gear unit, which is arranged in the interior space.

For lubricating the bearing 9, in particular the rolling bodies of the bearing 9, the first radial bore 3 is connected to the first spatial region. The oil delivered by the oil delivery device can thus pass through the first axial bore 8 through the housing part 1 into the first radial bore 3 and from there to the first spatial region 14, so that the bearings 9, in particular the rolling bodies of the bearings 9, can be supplied with lubricating oil.

In order to connect the first radial bore machined in the flange part 2 to the first spatial region 14, an axial bore extending through the flange part 2 from the first radial bore 3 opens into the first spatial region 14.

Since the first spatial region 14 is therefore at least partially filled with oil and directly adjoins the bearing 9, in particular the rolling elements of the bearing, a lubrication supply for the bearing 9 is ensured. However, the second labyrinth seal 11 is designed to be contactless. Further, a gap is formed between the flange member 2 and the shaft 6, so that there is no contact between the flange member 2 and the shaft 6. Therefore, it cannot be absolutely prevented that a small amount of oil may reach the second spatial region 7 along the surface of the shaft 6 via the second labyrinth seal 11. In particular, such undesired oil can therefore also be referred to as leakage oil.

As described above, this oil is then guided into the return by means of the projections 16, which act as draining and/or centrifuging edges. In addition, a first labyrinth seal 17 is also provided, so that a very high safety level is achieved with regard to the safety of the leakage oil.

The second labyrinth seal 11 is arranged axially between the bearing 9 or the first spatial region 14 and the second spatial region 7.

Between the two labyrinth seals, annular grooves and axially arranged projections 16 are arranged.

On the side of the first labyrinth seal 17 facing away from the second space region 7 in the axial direction, a further sealing ring, preferably designed as a V-ring 5, is arranged.

The V-ring is pushed onto the shaft 6 and is connected in a non-positive manner with the shaft and thus in a rotationally fixed manner. The sealing lip of the V-ring 5 extends over the finished flat sealing surface, wherein the normal of the plane containing the sealing surface is oriented parallel to the axial direction.

The axial direction is parallel to the direction of the axis of rotation of the shaft 6.

In a further embodiment, the cover plate is connected to the flange part 2, in particular by means of a screw, the threaded region of which is screwed into a threaded bore of the flange part 2 and the head of which presses the cover plate onto the flange part 2.

The cover plate covers the V-ring 5 here towards the surroundings. In particular, the radial length area covered by the cover plate includes the radial length area covered by the V-ring 5, except for the radial length area covered by the sealing lip of the shaft sealing ring 5.

The cover plate 1 serves as a protection for the V-ring 5 against dust particles.

A return, which comprises the second radial bore 12 of the flange part 2 and the second axial bore 13 through the housing part 1, is arranged in the lower region of the first spatial region. The return channel can be produced cost-effectively, since the return channel for the oil is formed on the flange part 2 in that the first spatial region 7 opens into a second radial bore 12 of the flange part 2, which opens into a second axial bore 13 of the housing part 1, which returns the oil to the oil sump, in particular together with the oil that comes into contact with the rolling bodies of the bearing 9.

In the oil sump, the heat input with the oil can then be dissipated and can be partially dissipated via the housing of the gear unit to the surroundings. The oil thus cooled can then be fed back to the first axial bore 8 of the housing part 1 by means of an active and/or passive oil supply. The oil flow thus delivered flows past the rolling bodies of the bearing 9.

The cover plate, the flange part 2 and the housing part 1 are made of metal, in particular steel.

For receiving the labyrinth seal, the flange part 2 has a corresponding support, which is finished, in particular ground and/or shaped accordingly. The labyrinth seal received on the support seals the flange part 2 in a contactless manner against the shaft 6.

For receiving the bearing 9, the housing part 1 has a bearing seat which is finished, in particular ground. A bearing 9 received in the seat supports the shaft 6.

The flange part 2 has a centering seat by means of which the flange part is centered on the bearing hole of the bearing 9. For this purpose, the bearing bore is arranged as a cylindrical recess in the housing part 1 of the gear unit and is finished, wherein the outer ring of the bearing 9 is pushed into the bearing seat thus produced. At the edge of the opening, which is preferably also finished, a cylindrical centering ring of the flange part 2 is pushed into the bearing bore. The flange part 2 is subsequently centered on the housing part 1 by means of the centering ring. However, the centering ring of the flange part 2 also serves as an axial stop for the outer ring of the bearing 9, which inner ring rests on the collar of the shaft 6.

The inner ring is retained in the axially opposite direction by means of a retaining ring arranged in a circumferential annular groove of the shaft 6.

In a further embodiment according to the invention, the flange part 2 is made of plastic in one piece, in particular in one piece, with the labyrinth seal. Preferably, to produce such a flange part 2 with an integrated labyrinth seal, an additive production method is carried out, in particular using a 3D printer. Preferably, the flange part 2 and the integrated labyrinth seal are made of plastic. Good thermal insulation between the first space region 14 and the second space region 7 can thus also be achieved.

Alternatively, the flange part 2 and the labyrinth seal can also be made of metal. Here, a sufficiently large gap exists between the labyrinth seal and the shaft 6 in order to prevent the shaft from contacting the sealing ring 4 in the event of transverse forces.

Embodiments of metals can also be produced additively, wherein correspondingly formed holes can then be provided instead of openings.

Claims (15)

1. A speed reducer having a shaft and a housing member,

wherein a bearing is received in the housing part, the bearing being used for rotatably supporting the shaft,

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

the flange member is connected to the housing member,

the flange part is sealed towards the shaft by means of a first labyrinth seal and a second labyrinth seal,

the first labyrinth seal is axially spaced from the second labyrinth seal,

the shaft has a projection which surrounds in the circumferential direction,

the projection is arranged between the first labyrinth seal and the second labyrinth seal in the axial direction.

2. A decelerator having a shaft and a housing member according to claim 1,

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

the first spatial area of the clearance is adjacent to the bearing,

the bearing can be supplied with lubricant from the first spatial region,

the first space region can be supplied with lubricant from a first radial bore of the flange part via a first axial bore running through the housing part, which first axial bore opens into the first radial bore.

3. A decelerator having a shaft and a housing member according to claim 2,

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

a second free space region is provided axially between the first labyrinth seal and the second labyrinth seal, which is delimited by the flange part, the first labyrinth seal, the second labyrinth seal and the shaft,

the second radial bore of the flange part opens into the second space region, wherein a second axial bore which penetrates the housing part opens into the second radial bore,

the second axial hole opens into the inner space of the reducer,

for returning oil from the second spatial region to the oil sump of the retarder.

4. A decelerator having a shaft and a housing member according to claim 3,

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

the projection is formed on the shaft and the second spatial region is arranged on the shaft in such a way that oil dripping or being thrown off from the projection reaches the second spatial region.

5. A decelerator having a shaft and a housing member according to claim 3,

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

the plug seals the first radial hole towards the second spatial region,

the first radial bore is sealed off from the environment by a further plug, the second radial bore being sealed off from the environment by a third plug.

6. A decelerator having a shaft and a casing member according to claim 1 or 2,

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

the projection is arranged axially between two circumferential grooves formed on the shaft and adjoining the projection.

7. A decelerator having a shaft and a casing member according to claim 1 or 2,

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

the maximum diameter of the shaft in the region of the shaft adjacent to the first of the annular grooves is equal to the maximum diameter of the shaft in the region covered by the projection in the axial direction,

the maximum diameter of the shaft in the region of the shaft adjacent to the second of the annular grooves is equal to the maximum diameter of the shaft in the region covered by the projection in the axial direction.

8. A decelerator having a shaft and a casing member according to claim 1 or 2,

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

the maximum diameter of the bearing seat of the inner ring of the bearing is equal to the maximum diameter of the shaft in the region covered by the projections in the axial direction.

9. A decelerator having a shaft and a housing member according to claim 3,

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

the first radial bore is designed as a stepped bore,

the plug is arranged in a narrowed region of the first radial bore, which narrowed region opens into the second space region,

the second radial bore is designed as a stepped bore.

10. A decelerator having a shaft and a housing member according to claim 2,

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

the oil flow delivered by the oil delivery device flows into the first radial hole.

11. A decelerator having a shaft and a housing member according to claim 10,

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

the oil transfer device has an oil pump driven by a motor or a shaft of the speed reducer, and has a collecting unit for collecting oil ejected upward in a rotational motion of a toothed member of the speed reducer, the oil being ejected in a direction opposite to a direction of gravity.

12. A decelerator having a shaft and a casing member according to claim 1 or 2,

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

the bearing is a radial thrust bearing, the shaft is a hollow shaft,

the shaft is the output shaft of the reducer, where the shaft is the largest diameter of all the shafts of the reducer.

13. A decelerator having a shaft and a housing member according to claim 3,

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

the flange part is formed integrally with the first labyrinth seal and/or the second labyrinth seal,

wherein the flange part together with the first labyrinth seal and/or the second labyrinth seal is produced from plastic as a plastic injection-molded part,

or wherein the flange part and the first labyrinth seal and/or the second labyrinth seal are made of metal,

or wherein the flange part and the first labyrinth seal and/or the second labyrinth seal are designed as additively manufactured components in which the first radial bore and the second radial bore are designed as shaped or additively formed channels, that is to say are not manufactured by means of an open-pored manner.

14. A decelerator having a shaft and a housing member according to claim 3,

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

on the side of the first labyrinth seal facing away from the second space region in the axial direction, a sealing ring is arranged, which is a V-ring,

the sealing ring is connected non-rotatably in a force-fitting manner to the shaft, and a sealing lip of the sealing ring extends over or seals against a finished, flat sealing surface formed on the flange part, wherein a normal of a plane containing the sealing surface is parallel to the axial direction.

15. A decelerator having a shaft and a casing member according to claim 1 or 2,

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

on the side of the flange part facing away from the bearing, a cover plate is connected to the flange part,

wherein the radial length region covered by the cover plate includes the radial length region covered by the seal ring, except for the gap between the cover plate and the shaft,

the sealing lip of the seal ring contacts the finished surface of the flange member and the cover plate is spaced from the shaft.

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