Speed reducer
By adopting double-row oblique tapered roller bearings and multi-blind hole design in the reducer, the problems of poor output shaft positioning and limited lubricant selection under high load are solved, and efficient reducer performance is achieved.
Patent Information
- Application Number
- CN202311078380.6
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Filing Date
- 2023-08-24
- Publication Date
- 2025-02-25
AI Technical Summary
Existing reducers have difficulty maintaining precise positioning of the output shaft under high load conditions, and lubricant selection is limited.
A reducer is designed with the output shaft supported by a double-row oblique tapered roller bearing and a number of blind holes are provided in the bearing housing to optimize heat dissipation and lubrication.
Reliable and precise positioning of the output shaft under high load conditions is achieved, and the overall performance of the reducer is improved by optimizing lubricant selection and heat dissipation design.
Smart Images
Figure CN119508465A_ABST
Abstract
Description
Technical Field
[0001] The invention relates to a reducer comprising a housing component and a bearing housing connected to the housing component. Background Art
[0002] It is known that a shaft is supported by means of at least two bearings which are axially spaced apart from one another. Summary of the invention
[0003] The object of the present invention is therefore to improve a reduction gear which has an output shaft which remains precisely positioned despite high loads.
[0004] This object is achieved according to the invention by a reduction gear according to the features specified in claim 1 .
[0005] In terms of the reducer, an important feature of the present invention is that the reducer is designed to have a housing member and a bearing housing connected to the housing member.
[0006] wherein the output shaft of the reducer is rotatably supported by means of a first bearing, the first bearing being received in the housing part, in particular wherein the outer ring of the first bearing is received in the housing part,
[0007] In particular, the inner ring of the first bearing is sleeved on the output shaft.
[0008] The output shaft of the reducer is rotatably supported by means of a second bearing, which is received in a bearing housing.
[0009] In particular, the outer ring of the second bearing is received in a bearing seat formed on the bearing housing,
[0010] In particular, the inner ring of the second bearing is sleeved on the output shaft.
[0011] In particular, the second bearing is designed as an X-shaped / face-to-face double-row angular contact bearing / radial thrust bearing / oblique bearing, in particular an oblique tapered roller bearing / angular contact tapered roller bearing or an oblique cylindrical roller bearing / angular contact cylindrical roller bearing.
[0012] The advantage here is that the output shaft can be supported by a second bearing, wherein the second bearing is arranged outside the housing part of the reducer and thus allows for a large bearing spacing. As a result, the position of the output shaft can be reliably ensured even under high loads. This is particularly advantageous if the output shaft is used in a precision grinding machine, in particular for producing wafers or the like, and is used to drive a grinding tool, in particular a grinding wheel.
[0013] Furthermore, the bearing can be arranged in a different lubricant than the gearing of the reducer. The lubricant can thus be selected in an optimal manner.
[0014] In an advantageous embodiment, a first shaft sealing ring is received in a flange connected to the housing part, the first shaft sealing ring sealing toward the output shaft, in particular a sealing lip of the first shaft sealing ring acts on and / or bears against a running surface of the output shaft.
[0015] The flange is arranged on a side of the housing part facing away from the bearing housing in the axial direction.
[0016] In particular, the flange and the housing part are connected in a sealed manner by means of an intermediately arranged seal, in particular a flat seal. The advantage here is that the shaft sealing ring is received in a separate flange and the heat loss of the shaft sealing ring can therefore be discharged separately.
[0017] In an advantageous design, a second shaft sealing ring is received in the bearing housing, which seals toward the output shaft, and in particular, a sealing lip of the second shaft sealing ring acts on and / or abuts against a running surface of the output shaft. An advantage of this is that the second shaft sealing ring is arranged axially between the first bearing and the second bearing. Thus, the two bearings can be supplied with different lubricants.
[0018] In an advantageous embodiment, the bearing housing is connected to the housing part in a sealed manner by means of another seal, in particular a flat seal, which is arranged between the bearing housing and the housing part. The advantage here is that lubricant can also be arranged inside the bearing housing and prevented from flowing out.
[0019] In an advantageous embodiment, the flange part is arranged on a side of the bearing housing facing away from the housing part and is connected to the bearing housing.
[0020] In this case, a third shaft sealing ring is received in the flange part, and the third shaft sealing ring seals toward the output shaft, and in particular, the sealing lip of the third shaft sealing ring acts on and / or abuts against the working surface of the output shaft. The advantage here is that the shaft sealing ring is received in a separate flange and thus the heat loss of the shaft sealing ring can be discharged separately.
[0021] In an advantageous embodiment, the output shaft has an externally threaded region, onto which a locking nut is screwed with its internal thread, the locking nut preloading the second bearing.
[0022] In particular, the locking nut presses the inner ring of the second bearing against the shoulder of the output shaft. The advantage here is that the bearing tension can be adjusted, wherein the locking nut can be arranged radially inside the flange part and can therefore be surrounded by the flange part in a housing-forming manner.
[0023] In an advantageous design, the area covered by the flange in the axial direction includes the area covered by the lock nut in the axial direction. Advantageously, the lock nut can be arranged radially inside the flange and can thus be surrounded by the flange in a manner to form a housing.
[0024] In an advantageous embodiment, a reversing transmission stage is arranged inside the housing part and is lubricated by a first lubricant, in particular lubricating oil.
[0025] In this case, a second lubricant, in particular a lubricating grease, is arranged inside the bearing housing. The advantage here is that the lubricant can be optimized for the respective application, ie the toothing or the cylindrical roller bearing.
[0026] In an advantageous embodiment, the housing part has an opening which is closed and / or covered by the gear unit cover. This has the advantage that simple assembly can be achieved.
[0027] In an advantageous design, the gear of the reversing transmission stage, in particular the bevel gear or the worm gear, is connected to the output shaft in a rotationally fixed manner and meshes with the bevel pinion or with the worm. The advantage here is that the transverse forces acting on the output shaft can be discharged through the second bearing.
[0028] In an advantageous embodiment, the outer diameter of the bearing housing, in particular the outer diameter of the bearing housing relative to the rotation axis of the output shaft, increases monotonically with increasing axial distance from the first bearing. This has the advantage that improved heat dissipation can be achieved by the surface increase thus produced.
[0029] In an advantageous embodiment, the radial wall thickness of the bearing housing, in particular the radial wall thickness of the bearing housing relative to the rotational axis of the output shaft, increases monotonically with increasing axial distance from the first bearing. This has the advantage that a high thermal capacity can be provided thereby.
[0030] In an advantageous embodiment, a plurality of radially oriented blind holes are formed in the bearing housing, in particular in the bearing seat of the second bearing.
[0031] In particular, the blind hole opens into a spatial region surrounded by the bearing flange and at least partially filled with the second lubricant, in particular, the corresponding opening is covered by the outer ring of the bearing,
[0032] In particular, the blind holes are spaced uniformly apart from one another in the circumferential direction and / or the blind holes are all arranged at the same axial position and / or the blind holes all have the same angle, in particular 90°, relative to the axis of rotation of the output shaft. This has the advantage that the mass of the bearing housing is reduced, while nevertheless providing a large surface for heat dissipation. Furthermore, the blind holes are at least partially filled with lubricant and thus act as a lubricant reservoir.
[0033] In an alternative advantageous embodiment, a plurality of blind holes are formed in the bearing housing, in particular in the bearing seat of the second bearing.
[0034] The hole axes of the blind holes each have an angle of 20° to 60° relative to the rotation axis of the output shaft.
[0035] In particular, the blind hole opens into a spatial region surrounded by the bearing flange and at least partially filled with the second lubricant, in particular, the corresponding opening is covered by the outer ring of the bearing,
[0036] In particular, the blind holes are spaced uniformly apart from one another in the circumferential direction and / or the blind holes are all arranged at the same axial position and / or the blind holes all have the same angle, in particular an angle of 45°, relative to the axis of rotation of the output shaft. This has the advantage that the mass of the bearing housing is reduced, while nevertheless providing a large surface for heat dissipation. Furthermore, the blind holes are at least partially filled with lubricant and thus act as a lubricant reservoir.
[0037] Further advantages are given by the dependent claims. The invention is not limited to the feature combinations of the claims. For a person skilled in the art, other reasonable combinations of the claims and / or the features of the individual claims and / or the features of the description and / or the features of the drawings are apparent, in particular from the objectives proposed and / or from a comparison with the prior art. BRIEF DESCRIPTION OF THE DRAWINGS
[0038] Now the present invention is described in detail according to the schematic diagram:
[0039] exist Figure 1 The reducer according to the present invention is shown in an oblique view.
[0040] exist Figure 2 A cross section of a reducer is shown in FIG.
[0041] List of reference numerals:
[0042] 1 Shell
[0043] 2 Bearing housing
[0044] 3 Output shaft
[0045] 4 reducer cover
[0046] 21 Worm
[0047] 22 Bearings, especially double row bearings
[0048] 23 Shaft sealing ring
[0049] 24 Lock nut
[0050] 25 Shaft sealing ring
[0051] 26 Shaft sealing ring
[0052] 27 Worm gear
[0053] 28 Flange
[0054] 29 Flange DETAILED DESCRIPTION
[0055] As shown in the figures, the reduction gear has a housing part 1 which surrounds an interior of the reduction gear which is at least partially filled with a lubricant, in particular lubricating oil.
[0056] The first transmission stage is designed as a worm gear stage. Here, the input shaft drives the worm wheel 27 by means of the worm 21 which is connected to the input shaft in a rotationally fixed manner.
[0057] The input shaft is rotatably supported by means of a bearing which is received in the housing part 1. Likewise, the worm gear 27 is connected in a rotationally fixed manner to the output shaft which is supported and rotatably supported by a bearing 20 received in the housing part 1 and a bearing 22 received in the bearing housing 2.
[0058] The first shaft sealing ring 26 seals the output shaft toward the housing part 1. The first shaft sealing ring 26 is received in a flange 29 which is connected to the housing part 1.
[0059] In order to precisely align the output shaft 3 , especially also under load, a separate, additional bearing unit is provided on the reducer, which has an X-arranged double-row oblique tapered roller bearing as the bearing 22 .
[0060] The bearing 22 is accommodated in the bearing housing 2. The bearing housing 2 has a fitting designed as a protruding journal region, which projects into a hole in the housing part 1. The bearing housing 2 thus rests on the housing part 1 and is connected sealingly by means of a flat seal arranged therebetween.
[0061] The second shaft sealing ring 25 seals the output shaft toward the bearing housing 2 on the side of the bearing housing 2 facing the worm wheel 27. Here, the second shaft sealing ring 25 is arranged in the journal region and / or the region covered by the second shaft sealing ring 25 in the axial direction overlaps with the region covered by the journal region in the axial direction or is contained in this region.
[0062] Therefore, the interior of the reducer, in particular the meshing region between the worm wheel 27 and the worm 21 , is at least partially filled with a first lubricant, in particular lubricating oil, and is sealed from the surrounding environment.
[0063] However, it is also possible to introduce a second lubricant, in particular grease, into the bearing housing, which lubricates the bearing 22 .
[0064] Therefore, on the side facing away axially from the second shaft sealing ring 25 , the flange part 28 is engaged in a bearing bore of the bearing housing 2 , in which the third shaft sealing ring 23 is accommodated, which likewise seals toward the output shaft 3 .
[0065] Also arranged inside the bearing housing 2 is a lock nut 24 , which is screwed with its internal thread onto an external thread formed on the output shaft and preloads the bearing 22 by pressing the lock nut against a shoulder of the output shaft 3 .
[0066] Therefore, the bearing stress can be adjusted by means of the lock nut 24 .
[0067] When manufacturing the reducer, after the lock nut 24 is screwed onto the output shaft 3 and the bearing stress of the bearing 22 is adjusted, the flange 28 is mounted and fixed to the bearing housing 2 with bolts. Therefore, the lock nut 24 is radially surrounded by the flange 28 and thus the second lubricant is applied. In particular, corrosion is prevented or at least reduced thereby.
[0068] The lock nut 24 rotates with the output shaft and is pressed onto the inner race or one of the inner races of the bearing 22 .
[0069] The output shaft 3 is preferably designed as a hollow shaft.
[0070] The first shaft sealing ring 26 is preferably designed as a shaft sealing ring pair.
[0071] The second shaft sealing ring 25 is preferably also designed as a shaft sealing ring pair.
[0072] The third shaft sealing ring 23 is preferably also designed as a shaft sealing ring pair.
[0073] The outer diameter of the output shaft 3 in the area of the third shaft sealing ring 23 , i.e. the running surface of the third shaft sealing ring on the output shaft, has a smaller radial spacing relative to the rotation axis of the output shaft 3 than the outer diameter of the output shaft 3 in the area of the second shaft sealing ring 25 , i.e. the running surface of the third shaft sealing ring 25 on the output shaft 3 .
[0074] What is important in the present invention is that the second shaft sealing ring 25 is not accommodated in the housing part of the reducer, but is accommodated in the bearing housing 2. Therefore, the heat loss generated in the second shaft sealing ring 25 is discharged to the surrounding environment through the bearing housing 2.
[0075] Therefore, a heat insulation device can also be arranged between the bearing housing 2 and the housing part 1, so that the housing part 1 only dissipates the heat of the first lubricant, that is, the heat loss from the meshing tooth part, and dissipates the heat loss of the first bearing 20 and the part of the first shaft sealing ring 26 received in the flange 29 connected to the housing part 1.
[0076] The outer diameter of the bearing housing 2 increases monotonically with increasing axial distance from the worm wheel 27 and / or from the first shaft sealing ring 26. Thus, improved heat dissipation to the surrounding environment can be achieved. This is because the bearing housing 2 has a radial wall thickness that increases monotonically with increasing distance from the worm wheel 27, at least in the region covered by the bearing 22 in the axial direction.
[0077] The axial direction is always parallel to the rotational axis of the output shaft 3. The radial direction and the circumferential direction are each based on the rotational axis of the output shaft 3. The high thermal capacity enables the interception of temperature peaks.
[0078] In another embodiment according to the present invention, a plurality of blind holes are formed in the bearing housing 2, which are radially oriented or obliquely oriented in such a way that the radial spacing of the blind holes increases with the increasing axial spacing from the first bearing 20. Therefore, the blind holes interrupt the bearing seat of the bearing 22.
[0079] The blind holes are spaced apart from one another in the circumferential direction, in particular spaced apart evenly.
[0080] Preferably, the hole axis of the blind hole is at an angle of between 20° and 60° relative to the rotation axis of the output shaft 3. As a result, the bearing housing 2 has a low mass and nevertheless has a high rigidity, so that even when high lateral forces are introduced into the output shaft 3 on the load side, the spatial orientation of the output shaft remains essentially constant. In addition, the blind hole is at least partially filled with a second lubricant, thereby reducing or at least reducing corrosion. Alternatively, the blind hole can be filled with a heat-conducting paste, which hardens in particular after filling and does not chemically bond to the lubricant or dissolve in the lubricant. This heat-conducting paste can also be mixed with an adhesive, which causes a material-locked connection between the outer ring of the bearing 22 and the bearing housing 2. As a result, the outer ring of the bearing 22 cannot rotate relative to the bearing housing 2.
[0081] The blind hole thus also serves as a lubricant reservoir, since the outer ring received in the bearing seat does not completely close the access opening of the blind hole.
[0082] In a further exemplary embodiment according to the invention, a further reversing gear stage, in particular a bevel gear stage, is used instead of the worm gear stage, wherein the worm 21 is then replaced by a bevel pinion and the worm wheel 27 by a bevel gear.
Claims
1. A reducer comprising a housing member and a bearing housing connected to the housing member, The output shaft of the reducer is rotatably supported by means of a first bearing, which is received in the housing component, and in particular, the outer ring of the first bearing is received in the housing component. In particular, the inner ring of the first bearing is mounted on the output shaft. It is characterized in that The output shaft of the reducer is rotatably supported by means of a second bearing, which is received in a bearing housing. In particular, the outer ring of the second bearing is received in a bearing seat formed on the bearing housing. In particular, the inner ring of the second bearing is mounted on the output shaft. In particular, the second bearing is designed as an X-shaped double-row angular contact bearing, in particular, an inclined tapered roller bearing or an inclined cylindrical roller bearing.
2. The reducer according to claim 1, It is characterized in that A first shaft sealing ring is received in a flange connected to the housing part, the first shaft sealing ring sealing toward the output shaft, in particular a sealing lip of the first shaft sealing ring acts on and / or bears against a running surface of the output shaft, The flange is arranged on the side of the housing part facing away from the bearing housing in the axial direction. In particular, the flange is connected to the housing part in a sealing manner by means of a seal arranged in between, in particular a flat seal.
3. A reducer according to any one of the preceding claims, It is characterized in that A second shaft sealing ring is accommodated in the bearing housing and seals toward the output shaft, in particular a sealing lip of the second shaft sealing ring acts on and / or bears against a running surface of the output shaft.
4. A reducer according to any one of the preceding claims, It is characterized in that The bearing housing and the housing part are connected sealingly by means of a further seal, in particular a flat seal, which is arranged between the bearing housing and the housing part.
5. A reducer according to any one of the preceding claims, It is characterized in that A flange part is arranged on the side of the bearing housing facing away from the housing part and is connected to the bearing housing. A third shaft sealing ring is accommodated in the flange part, which seals toward the output shaft, in particular a sealing lip of the third shaft sealing ring acts on and / or bears against a running surface of the output shaft.
6. A reducer according to any one of the preceding claims, It is characterized in that The output shaft has an external threaded area, onto which a lock nut is screwed with its internal thread, and the lock nut preloads the second bearing. In particular, this is done in that the lock nut presses the inner ring of the second bearing against a shoulder of the output shaft.
7. A reducer according to any one of the preceding claims, It is characterized in that The area covered by the flange in the axial direction includes the area covered by the lock nut in the axial direction.
8. A reducer according to any one of the preceding claims, It is characterized in that A reversing transmission stage is arranged inside the housing part and is lubricated by a first lubricant, in particular lubricating oil. A second lubricant, in particular grease, is arranged inside the bearing housing.
9. A reducer according to any one of the preceding claims, It is characterized in that The housing part has an opening which is closed and / or covered by the gear unit cover.
10. A reducer according to any one of the preceding claims, It is characterized in that The gear of the reversing gear stage, in particular a bevel gear or a worm gear, is connected to the output shaft in a rotationally fixed manner and meshes with a bevel pinion or with a worm.
11. A reducer according to any one of the preceding claims, It is characterized in that The outer diameter of the bearing housing, in particular the outer diameter of the bearing housing relative to the rotational axis of the output shaft, increases monotonically with increasing axial distance from the first bearing.
12. A reducer according to any one of the preceding claims, It is characterized in that The radial wall thickness of the bearing housing, in particular the radial wall thickness of the bearing housing relative to the rotational axis of the output shaft, increases monotonically with increasing axial distance from the first bearing.
13. A reducer according to any one of the preceding claims, It is characterized in that A plurality of radially oriented blind holes are formed in the bearing housing, in particular in the bearing seat of the second bearing, In particular, the blind hole opens into a spatial region surrounded by the bearing flange and at least partially filled with the second lubricant, in particular the corresponding opening is covered by the outer ring of the bearing, In particular, the blind holes are evenly spaced apart from one another in the circumferential direction and / or the blind holes are all arranged at the same axial position and / or the blind holes all have the same angle, in particular 90°, relative to the rotation axis of the output shaft.
14. The reducer according to any one of claims 1 to 12, It is characterized in that A plurality of blind holes are formed in the bearing housing, in particular in the bearing seat of the second bearing. The hole axes of the blind holes each have an angle between 20° and 60° with respect to the rotation axis of the output shaft. In particular, the blind hole opens into a spatial region surrounded by the bearing flange and at least partially filled with the second lubricant, in particular the corresponding opening is covered by the outer ring of the bearing, In particular, the blind holes are evenly spaced apart from one another in the circumferential direction and / or the blind holes are all arranged at the same axial position and / or the blind holes all have the same angle, in particular 45°, relative to the rotation axis of the output shaft.