阅读说明：本技术 具有锥齿轮传动级和壳体的减速器 (Speed reducer with bevel gear stage and housing ) 是由 S·汉尼特 于 2020-03-12 设计创作，主要内容包括：本发明涉及一种具有锥齿轮传动级和壳体的减速器,锥齿轮传动级的第一有齿部件与轴以不能相对转动的方式连接,轴与第一有齿部件共同通过第一轴承并通过第二轴承以能转动的方式被支承,第一轴承被接纳在壳体中,第二轴承被接纳在壳体中,壳体具有第一内螺纹部段和与第一内螺纹部段轴向间隔开的第二螺纹部段,旋拧到第一内螺纹部段中的螺母特别是在轴向方向上压到第一轴承的外环上,第一轴承的内环抵靠阶梯部,旋拧到第二内螺纹部段中的螺母特别是反向于轴向方向压到第二轴承的外环上,第二轴承的内环抵靠第一有齿部件、特别是抵靠第一有齿部件的阶梯部,或者抵靠轴的阶梯部。(The invention relates to a reduction gear having a bevel gear stage and a housing, a first toothed part of the bevel gear stage being connected in a rotationally fixed manner to a shaft, the shaft together with the first toothed part being rotatably supported by a first bearing and by a second bearing, the first bearing being received in the housing, the second bearing is received in a housing having a first internal thread section and a second thread section axially spaced apart from the first internal thread section, a nut screwed into the first internal thread section pressing in particular in an axial direction onto an outer ring of the first bearing, the inner ring of the first bearing abutting the step, a nut screwed into the second internal thread section pressing in particular counter to the axial direction onto an outer ring of the second bearing, the inner ring of the second bearing abutting the first toothed member, in particular the step of the first toothed member, or the step of the shaft.)

1. A reduction gear having a bevel gear stage and a housing,

the first toothed part of the bevel gear stage is connected to the shaft in a rotationally fixed manner,

the shaft is rotatably supported together with the first toothed member by a first bearing and by a second bearing,

the first bearing is received in the housing, the second bearing is received in the housing,

the housing has a first internally threaded section and a second threaded section axially spaced from the first internally threaded section,

the nut screwed into the first internally threaded section is pressed, in particular in the axial direction, onto the outer ring of the first bearing,

the inner ring of the first bearing abuts against the step of the shaft,

the nut screwed into the second internally threaded section presses, in particular counter to the axial direction, onto the outer ring of the second bearing,

the inner ring of the second bearing abuts against the first toothed part, in particular against the step of the first toothed part, or against the step of the shaft.

2. A decelerator according to claim 1 wherein the decelerator is provided with,

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

the first nut is arranged on a side of the first bearing facing away from the second bearing.

3. A decelerator according to any preceding claim,

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

the second nut is arranged on a side of the second bearing facing away from the first bearing.

4. A decelerator according to any preceding claim,

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

the first bearing is a skewed bearing, in particular a cylindrical roller bearing or a tapered roller bearing,

and/or

The second bearing is a skewed bearing, in particular a cylindrical roller bearing or a tapered roller bearing.

5. A decelerator according to any preceding claim,

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

the shell includes a first shell member having a first threaded section and a second shell member having a second threaded section,

the first housing part is connected to the second housing part by means of a screw.

6. A decelerator according to any preceding claim,

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

a cover element is received in the second nut, in particular in an axially through opening of the second nut, which is arranged centrally in the second nut, said cover element closing off and/or covering the axially through opening arranged centrally in the second nut, in particular in an oil-tight manner,

alternatively, a shaft sealing ring is received in the second nut, in particular in an axially through opening of the second nut arranged centrally in the second nut, which shaft sealing ring is sealed or covered toward the shaft, in particular in an oil-tight manner.

7. A decelerator according to any preceding claim,

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

in the first nut, in particular in an axially through opening of the first nut, which is arranged centrally in the first nut, a shaft sealing ring is received, which is sealed or covered toward the shaft, in particular in an oil-tight manner.

8. A decelerator according to any preceding claim,

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

the first toothed member meshes with the second toothed member,

in particular wherein the axis of rotation of the first toothed member is perpendicular to the axis of rotation of the second toothed member.

9. A decelerator according to any preceding claim,

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

the bevel gear stage is a hypoid gear stage or a helical face gear stage.

10. A decelerator according to any preceding claim,

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

in particular, neglecting the groove for receiving the stop ring, the outer diameter of the shaft decreases monotonically, in particular in steps, in the axial direction, in particular between the first bearing and the second bearing,

in particular wherein the inner ring of the first bearing abuts against the stop ring, and/or wherein the inner ring of the first bearing is pressed onto the stop ring by means of at least one adjusting shim arranged in the middle,

or

In particular, if the groove for receiving the locking ring is omitted, in particular from the first end side of the shaft, the outer diameter of the shaft increases monotonically, in particular stepwise, in the axial direction to a maximum value, in particular to a maximum plateau, and then decreases to an axial end region, in particular to the other end side of the shaft,

in particular, the inner ring of the first bearing abuts against the stop ring and/or is pressed onto the stop ring by means of at least one adjusting shim arranged in the middle.

11. Method for manufacturing a retarder, in particular according to one of the preceding claims,

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

in a first method step, the bearing preload of the two bearings is adjusted by screwing the nuts, i.e. the nuts are actuated, in particular screwed, in particular asynchronously,

in a second method step, which is carried out temporally after the first method step, the nuts are actuated synchronously, in particular rotated by synchronous screwing, in order to adjust the axial play between the two toothed elements, in particular to minimize the axial play between the two toothed elements.

Technical Field

The invention relates to a reduction gear having a bevel/reversing gear stage and a housing.

Background

Shims are known for adjusting the desired position of components.

As the closest prior art, DE 102015200741 a1 discloses a reduction gear and a method for adjusting the rotational play of the reduction gear.

A method for adjusting the pretension of a bearing is known from document US 2012/0295753 a 1.

A hub bearing is known from DE 9216915U 1.

A differential is known from document US 3260132 a.

A standard retarder is known from DE 10256752C 5.

A reduction gear is known from DE 102008026806 a 1.

Disclosure of Invention

The object of the invention is therefore to improve a reduction gear having a bevel/reversing gear stage and a housing, wherein the service life is to be increased.

According to the invention, this object is achieved by a reduction gear having a bevel gear stage and a housing according to the features specified in claim 1.

In a reduction gear unit having a bevel gear stage and a housing, the essential feature of the invention is that the first toothed part of the bevel gear stage is connected to the shaft in a rotationally fixed manner,

wherein the shaft is rotatably supported together with the first toothed member by a first bearing and by a second bearing,

wherein the first bearing is received in the housing, the second bearing is received in the housing,

wherein the housing has a first internally threaded section and a second threaded section axially spaced therefrom,

wherein the nut screwed into the first internally threaded section presses, in particular in the axial direction, onto the outer ring of the first bearing,

wherein the inner ring of the first bearing abuts against the step of the shaft,

wherein the nut screwed into the second internally threaded section is pressed, in particular counter to the axial direction, onto the outer ring of the second bearing,

wherein the inner ring of the second bearing abuts against the first toothed member, in particular against the step of the first toothed member, or against the step of the shaft.

This has the advantage that no spacer washers or adjusting shims are required to adjust the bearing pretension/bearing stress. Since the bearing preload can be adjusted by asynchronous screwing of the two nuts and the play of the bevel gear stages can be adjusted by synchronous screwing. Therefore, by simply selecting the screwing mode, the bearing pretightening force or the gap can be adjusted.

In an advantageous embodiment, the first nut is arranged on the side of the first bearing facing away from the second bearing. The advantage here is that the nut can be actuated from the outside.

In an advantageous embodiment, the second nut is arranged on the side of the second bearing facing away from the first bearing. The advantage here is that the nut can be actuated from the outside.

In an advantageous embodiment, the first bearing is a tapered bearing, in particular a cylindrical roller bearing or a tapered roller bearing, and the second bearing is a tapered bearing, in particular a cylindrical roller bearing or a tapered roller bearing. The advantage here is that high bearing pretension can be set.

In an advantageous embodiment, the housing comprises a first housing part having a first threaded portion and a second housing part having a second threaded portion,

wherein the first housing part is connected to the second housing part by means of a screw element. The advantage here is that a simplified assembly can be achieved if the shaft diameter of the shaft extends non-monotonically in the axial direction.

In an advantageous embodiment, a cover is received in the second nut, in particular in an axially through-going opening of the second nut arranged centrally in the second nut, said cover closing and/or covering the axially through-going opening arranged centrally in the second nut, in particular in an oil-tight manner,

alternatively, a shaft sealing ring, which is sealed or covered, in particular oil-tight, against the shaft, is received in the second nut, in particular in an axially through opening of the second nut, which is arranged centrally in the second nut. The advantage here is that one of the two axial end regions of the shaft can be covered, i.e. can be enclosed in such a way that a housing is formed.

In an advantageous embodiment, a shaft sealing ring, which is sealed or covered, in particular oil-tightly, against the shaft, is received in the first nut, in particular in an axially through opening of the first nut, which opening is arranged centrally in the first nut. The advantage here is that the shaft projects axially outward through the shaft sealing ring and is sealed axially outward.

In an advantageous embodiment, the first toothed element meshes with the second toothed element,

in particular wherein the axis of rotation of the first toothed member is perpendicular to the axis of rotation of the second toothed member. The advantage here is that the play of the bevel gear stage according to the invention is adjustable.

In an advantageous embodiment, the bevel gear stage is a hypoid gear stage or a helical flat gear stage (spiroplangetriebsufe). The advantage here is that the service life and the efficiency of the bevel gear stage can be optimized by means of the play adjustment, which in particular minimizes play.

In an advantageous embodiment, in particular in the case of omission of the groove for receiving the locking ring/safety ring, in particular between the first bearing and the second bearing, the outer diameter of the shaft decreases monotonically, in particular in steps, in the axial direction,

in particular wherein the inner ring of the first bearing abuts against the stop ring and/or wherein the inner ring of the first bearing is pressed onto the stop ring by means of at least one adjusting shim arranged in the middle. The advantage here is that a simple assembly can be achieved.

In an advantageous embodiment, in particular in the case of a groove for receiving a locking ring being omitted, in particular from a first end face of the shaft, the outer diameter of the shaft increases monotonically, in particular stepwise, in the axial direction to a maximum value, in particular to a maximum plateau, and then decreases until an axial end region, in particular the other end face of the shaft,

in particular wherein the inner ring of the first bearing abuts against the stop ring and/or wherein the inner ring of the first bearing is pressed onto the stop ring by means of at least one adjusting shim arranged in the middle. The advantage here is that an assembly from both axial sides can be achieved.

An important feature in the method for producing a gear unit is that in a first method step, the bearing preload of the two bearings is adjusted by screwing the nuts, i.e. the nuts are actuated, in particular screwed, out of phase,

in a second method step, which is carried out after the first method step in terms of time, the nuts are actuated synchronously, in particular rotated by synchronous screwing, in order to adjust, in particular minimize, the axial play between the two toothed parts.

The advantage here is that the bearing preload or play in the bevel gear stage can be adjusted by means of a purely selective actuation. The bearing pretension can be adjusted by asynchronous screwing of the nut and the bearing play can be adjusted by synchronous screwing.

Further advantages are given by the dependent claims. The invention is not limited to the combination of features of the claims. Other possible combinations of the features of the claims and/or of the individual claims and/or of the features of the description and/or of the drawings can be made possible for the person skilled in the art, in particular from the objects set forth and/or by comparison with the prior art.

Drawings

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

fig. 1 shows a cross section of the region of the first gear stage of the gear unit, wherein a cover 9 is received in the first nut 9 as a press-in cover (Einschlagdeckel).

Fig. 2 shows a further reduction gear according to the invention, wherein, in contrast to fig. 1, the shaft 20 in the reduction gear has a diameter which increases monotonically in the axial direction.

Fig. 3 shows a further reduction gear according to the invention, wherein, in contrast to fig. 1 and 2, instead of the cover 9, a shaft sealing ring 31 is received in the nut 8.

Detailed Description

As shown in fig. 1, the housing of the gear unit is formed in at least two parts. For this purpose, the first housing part 4 is screwed to the second housing part 5, wherein a connecting screw, the screw head of which presses the second housing part 5 onto the first housing part 4, passes through an opening, in particular a bore, which extends through the second housing part 5 and is screwed into an axially directed threaded bore of the first housing part 4.

A first bearing 2 is received in the first housing part 4 for rotatably supporting the shaft 1.

The first bearing 2 is preferably designed as a skewed bearing, in particular as a tapered roller bearing.

The first toothed element 6, in particular a crown gear, is connected to the shaft 1 in a rotationally fixed manner.

The teeth of the first toothed element 6 mesh with the teeth of the second toothed element 10, which is axially abutted against the shaft step of the shaft 1 and is thus limited in the axial direction.

The first housing part 4 has an internal thread section into which the nut 3 is screwed with its external thread. The axial position of the nut, i.e. the position of the nut in the direction of the axis of rotation of the shaft, is changed by means of the screwing of the nut 3.

The first bearing 2 received in the first housing part 4 has an outer ring onto which the nut 3 is pressed, in particular in the axial direction.

Since the inner ring of the bearing 2 is pressed against the shaft step of the shaft 1, the bearing 2, in particular its outer ring, can be displaced or at least the bearing preload can be adjusted by screwing the nut 3.

A shaft sealing ring 11 is received centrally in the nut 3, which shaft sealing ring seals towards the shaft 1. For this purpose, the nut 3 has an opening running through in the axial direction, in which opening the shaft sealing ring 11 is fitted and the inner diameter of which is greater than the outer diameter of the shaft 1.

The first toothed element 6 is designed as a hub and is fitted onto the shaft 1. Here, it rests with a step formed on the inner wall of the hub, which runs around in the circumferential direction, against a shaft step of the shaft 1. It is preferably also possible to achieve that the radially inwardly projecting lug regions formed on the first toothed part 6 bear in a positive-locking manner in the circumferential direction against corresponding radially directed recesses on the circumference of the shaft 1, so that a positive-locking action in the circumferential direction can thus be formed.

On the side of the toothing of the first toothed element 6 facing away from the first housing part 4, a second bearing 7 is slipped onto the first toothed element 6.

The inner ring of the second bearing 7 abuts against the step of the first toothed member 6.

The second housing part 5 likewise has an internal thread section into which the second nut 8 is screwed with its external thread. The axial position of the nut, i.e. the position of the nut in the direction of the axis of rotation of the shaft, is changed by means of the screwing of the nut 8.

The first bearing 7 received in the first housing part 5 has an outer ring onto which the second nut 8 is pressed, in particular counter to the axial direction.

Since the inner ring of the bearing 7 rests on the step of the first toothed element 6, the bearing 7, in particular its outer ring, can be displaced or at least the bearing preload can be adjusted by screwing the second nut 8.

Thus, by the simultaneous screwing of the two nuts 3 and 8, the first toothed member 6 can move axially together with the shaft 1 and the bearings 2 and 7.

In the second nut 8, a cover 9 is received in an axially through-going opening which is configured centrally in the second nut 8. The cover 9 seals the opening in a sealing manner, in particular oil-tight.

The play of the gear stages can be adjusted, in particular minimized, by means of the simultaneous screwing movement of the two nuts 3 and 8.

When the first toothed element 6 is moved, the second toothed element 10 does not move, but remains axially unchanged. The second toothed part 5 is connected to a shaft which is supported by further bearings which are axially fixed relative to the second housing part 5.

The axis of rotation of the second toothed member 10 is perpendicular to the axial direction, i.e. also to the axis of rotation of the first toothed member 6.

The toothed elements 6 and 10 thus form a bevel gear stage.

Preferably, the bevel gear stage is designed as a helical flat gear stage or as a hypoid gear stage. The adjustment of the minimum gap is particularly important for achieving a long service life.

During the assembly of the gear unit, in a first method step, the bearing pretension of the two bearings (2, 7) is set, in particular by asynchronous screwing of the nuts 3 and 8. Only after the bearing preload has been set is the play between the two toothed parts 6 and 10 reduced by: the nuts 3 and 8 are screwed simultaneously, i.e. they are operated in the same direction of rotation and at the same angular speed or are rotated at least by the same angular value.

The shaft has an outer diameter in the axial direction which first increases monotonically, in particular in a step-like manner, until a maximum value, in particular a maximum plateau, is reached which is arranged axially between the two bearings (2, 7), and then has an outer diameter which decreases monotonically, in particular in a step-like manner.

On the input side, i.e. on the side of the bearing 2 facing away from the second bearing 7, there is a smaller shaft diameter than in the region of the other end of the shaft 1.

The first bearing 2, in particular the inner ring of the first bearing 2, has a smaller inner diameter than the second bearing 7. Therefore, the loss power generated at the input side is small.

As shown in fig. 2, the shaft has a monotonically decreasing, in particular stepwise decreasing, outer diameter counter to the axial direction, so that the two bearings 2 and 7 are approximately equally large, since the difference in the shaft diameter is compensated by the wall thickness of the first toothed element 6 designed as a hub.

In fig. 2, the shaft is also covered by a cover 9 at its end region, which is arranged opposite to the axial direction, so that the shaft 1 is not led out.

The cover member 9 is preferably made of steel plate.

As shown in fig. 3, the shaft is guided out there on both sides, so that on the output side a shaft sealing ring 31 received in the second nut 8 seals against the shaft 1.

The shaft 1 also has an outer diameter which decreases monotonically, in particular in a stepped manner, in the direction opposite to the axial direction.

As shown in fig. 2 and 3, respectively, the monotonic change in the outer diameter is to be understood as excluding a groove for arranging a stop ring against which the inner ring of the first bearing 2 abuts and/or wherein the inner ring of the first bearing 2 is pressed onto the stop ring by means of at least one adjusting shim arranged in the middle.

Although the inner ring of the first bearing 2 abuts the step of the shaft on its side facing away from the stop ring and/or the spacer; however, this can also be achieved without force action and/or with play, since the pretensioning force is transmitted via the snap ring. The step of the shaft serves only for the form-locking fixing of the inner ring between the stop ring and the step.

In an alternative embodiment, instead of a monotonically decreasing change in the outer diameter, a monotonically increasing change in the outer diameter can also be achieved without the groove for receiving a stop ring against which the inner ring of the bearing abuts and/or wherein the inner ring is pressed onto the stop ring by means of at least one adjusting shim arranged in the middle.

In other embodiments according to the invention, the cover 9 is preferably made of plastic.

List of reference numerals:

1 axle

2 first bearing

3 nut

4 first housing part

5 second housing part

6 first toothed part, in particular crown gear

7 second bearing

8 nut

9 cover element

10 second toothed part, in particular bevel pinion

11 shaft sealing ring

20 shaft

30-shaft, in particular hollow shaft

31 shaft sealing ring