Gearing comprising a housing part and a bearing housing connected to the housing part

Abstract

The invention relates to a gearing comprising a housing part and a bearing housing connected to the housing part, wherein a driven shaft of the gearing is rotatably mounted by means of a first bearing which is accommodated in the housing part, in particular wherein an outer race of the first bearing is accommodated in the housing part, in particular wherein the inner race of the first bearing is fitted onto the driven shaft, and wherein the driven shaft of the gearing is rotatably mounted by means of a second bearing which is accommodated in the housing part.

Description

[0001] Gearbox with a housing part and a bearing housing connected to the housing part

[0002] Description:

[0003] The invention relates to a transmission with a housing part and a bearing housing connected to the housing part.

[0004] It is generally known that a shaft is supported by at least two axially spaced bearings.

[0005] The closest prior art known from CN 2 682 250 Y is a gearbox with a housing part.

[0006] An angular gear is known from CN 1 06438 973 A.

[0007] An angular gear is known from CN 2 04 985 521 U.

[0008] An axially offset angular gear is known from DE 43 09 559 A1.

[0009] A worm gear is known from DE 102009 005 346 A1.

[0010] A gearbox is known from DE 102009 014 314 A1.

[0011] DE 102020 001 269 A1 discloses a method for producing different transmissions.

[0012] A bearing arrangement is known from US 2008 / 0 124 014 A1.

[0013] A series of drive systems is known from DE 100 59 503 A1.

[0014] A double-row bearing arrangement for a wind turbine is known from JP 2006-214 545 A. The invention is therefore based on the object of developing a gearbox with an output shaft that remains precisely positioned despite high loads.

[0015] According to the invention, the object is achieved in the transmission according to the features specified in claim 1 or 2.

[0016] Important features of the invention in the transmission are that the transmission is designed with a housing part and a bearing housing connected to the housing part, wherein an output shaft of the transmission is rotatably mounted by means of a first bearing which is received in the housing part, in particular wherein an outer ring of the first bearing is received in the housing part, in particular wherein the inner ring of the first bearing is placed on the output shaft, wherein the output shaft of the transmission is rotatably mounted by means of a second bearing which is received in the bearing housing, in particular wherein an outer ring of the second bearing is received on a bearing seat formed on the bearing housing, in particular wherein the inner ring of the second bearing is placed on the output shaft, in particular wherein the second bearing is designed as a double-row angular contact bearing, in particular an angular contact tapered roller bearing or angular contact cylindrical roller bearing, in an X arrangement.

[0017] The advantage here is that the output shaft can be supported by the second bearing, with this second bearing being located outside the housing part of the gearbox, thus allowing a large bearing spacing. This ensures that the position of the output shaft is reliably maintained even under high loads. This is particularly advantageous when the output shaft is used in a precision grinding machine, particularly for the production of wafers or the like, and drives the grinding tool, in particular the grinding wheel. Furthermore, the bearing can be provided with a different lubricant than the gear teeth. The lubricant can therefore be selected in an optimized manner.

[0018] In an advantageous embodiment, a first shaft seal is accommodated in a flange connected to the housing part, which seals against the output shaft, in particular its sealing lip runs on and / or bears against a running surface of the output shaft. The flange is arranged on the side of the housing part axially facing away from the bearing housing, in particular the flange is sealed to the housing part by means of an intermediate seal, in particular a flat seal. It is advantageous that the shaft seal is accommodated in a separate flange, thus allowing its heat loss to be dissipated separately.

[0019] In an advantageous embodiment, a second shaft seal is accommodated in the bearing housing, which seals against the output shaft, in particular, its sealing lip runs on and / or bears against a running surface of the output shaft. Advantageously, the second shaft seal is arranged axially between the first bearing and the second bearing. This allows the two bearings to be supplied with different lubricants.

[0020] In an advantageous embodiment, the bearing housing is sealed to the housing part by means of an additional seal, in particular a flat seal, arranged between the bearing housing and the housing part. This is advantageous because a lubricant can also be provided within the bearing housing, preventing lubricant leakage.

[0021] In an advantageous embodiment, a flange part is arranged on the side of the bearing housing facing away from the housing part and connected to the bearing housing. A third shaft seal is accommodated in the flange part, which seals against the output shaft, in particular, its sealing lip runs on and / or bears against a running surface of the output shaft. Advantageously, the shaft seal is accommodated in a separate flange, allowing its heat loss to be dissipated separately.

[0022] In an advantageous embodiment, the output shaft has an external threaded portion onto which a clamping nut is screwed with its internal thread. This clamping nut preloads the second bearing, in particular by pressing an inner ring of the second bearing toward a shaft collar of the output shaft. Advantageously, the bearing tension is adjustable, with the clamping nut being arranged radially within the flange portion and thus being surrounded by the flange portion to form a housing.

[0023] In an advantageous embodiment, the area covered by the clamping nut in the axial direction is encompassed by the area covered by the flange part in the axial direction. Advantageously, the clamping nut can be arranged radially within the flange part and thus can be surrounded by the flange part to form a housing.

[0024] In an advantageous embodiment, an angular gear stage is arranged within the housing part, which is lubricated by a first lubricant, in particular lubricating oil, while a second lubricant, in particular lubricating grease, is arranged within the bearing housing. An advantage here is that the lubricants can be optimized for the respective application, i.e., tooth engagement or cylindrical roller bearings.

[0025] In an advantageous embodiment, the housing part has an opening that is closed and / or covered by a gear cover. This is advantageous because it enables easy assembly.

[0026] In an advantageous embodiment, a gear, in particular a bevel gear or a worm gear, of the angular gear stage is connected in a rotationally fixed manner to the output shaft and meshes with a bevel pinion or a worm. Advantageously, the transverse forces acting on the output shaft can be dissipated via the second bearing.

[0027] In an advantageous embodiment, the outer diameter of the bearing housing, in particular the outer diameter of the bearing housing relative to the axis of rotation of the output shaft, increases monotonically with increasing axial distance from the first bearing. The advantage here is that the resulting surface enlargement allows for improved heat dissipation.

[0028] 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 axis of rotation of the output shaft, increases monotonically with increasing axial distance from the first bearing. The advantage of this is that a high heat capacity can be provided.

[0029] In an advantageous embodiment, radially directed blind holes are formed in the bearing housing, in particular in the bearing seat of the second bearing, in particular wherein the blind holes open into the space surrounded by the bearing flange and at least partially filled with the second lubricant, in particular wherein the respective opening is covered by an outer ring of the bearing, in particular wherein the blind holes are evenly spaced from one another in the circumferential direction and / or wherein the blind holes are all arranged at the same axial position and / or wherein the blind holes all have the same angle to the axis of rotation of the output shaft, in particular 90°. The advantage here is that the mass of the bearing housing is reduced and yet a large surface area is provided for heat dissipation. In addition, the blind holes are at least partially filled with lubricant and thus function as a lubricant reservoir.

[0030] In an alternative advantageous embodiment, blind holes are introduced into the bearing housing, in particular into the bearing seat of the second bearing, wherein the hole axes of the blind holes each have an angle of between 20° and 60° to the axis of rotation of the output shaft, in particular wherein the blind holes open into the space surrounded by the bearing flange and at least partially filled with the second lubricant, in particular wherein the respective opening is covered by an outer ring of the bearing, in particular wherein the blind holes are evenly spaced from one another in the circumferential direction and / or wherein the blind holes are all arranged at the same axial position and / or wherein the blind holes all have the same angle to the axis of rotation of the output shaft, in particular 45°. The advantage here is that the mass of the bearing housing is reduced and yet a large surface area is provided for heat dissipation.In addition, the blind holes are at least partially filled with lubricant and thus function as a lubricant reservoir.

[0031] Further advantages emerge from the dependent claims. The invention is not limited to the combination of features in the claims. Further possible combinations of claims and / or individual claim features and / or features of the description and / or the figures will become apparent to those skilled in the art, particularly from the problem and / or the problem posed by comparison with the prior art.

[0032] The invention will now be explained in more detail using schematic illustrations:

[0033] Figure 1 shows an oblique view of a transmission according to the invention.

[0034] Figure 2 shows a cross-section of the gearbox.

[0035] As shown in the figures, the transmission has a housing part 1 which surrounds the interior of the transmission which is at least partially filled with lubricant, in particular lubricating oil.

[0036] The first gear stage is designed as a worm gear stage. The input shaft drives a worm gear 27 via a worm 21 that is non-rotatably connected to the input shaft.

[0037] The input shaft is rotatably mounted by means of bearings accommodated in the housing part 1. Likewise, the worm gear 27 is non-rotatably connected to an output shaft via a bearing 20 accommodated in the housing part 1 and a bearing 22 that is accommodated and rotatably mounted in the bearing housing 2.

[0038] A first shaft seal 26 seals the output shaft to the housing part 1. The first shaft seal 26 is accommodated in a flange 29, which is connected to the housing part 1.

[0039] For precise alignment of the output shaft 3, especially under load, a separate additional bearing unit is provided on the gearbox, which has a double-row angular contact tapered roller bearing in an X arrangement as bearing 22.

[0040] The bearing 22 is accommodated in the bearing housing 2. The bearing housing 2 has a fitting designed as a protruding journal area that projects into a bore in the housing part 1. The bearing housing 2 thus rests against the housing part 1 and is tightly connected by means of an intermediate flat seal. A second shaft seal 25 seals the output shaft on the side of the bearing housing 2 facing the worm gear 27 towards the bearing housing 2. The second shaft seal 25 is arranged in the journal area and / or the area covered in the axial direction by the second shaft seal 25 overlaps with the area covered in the axial direction by the journal area or is contained in it.

[0041] Thus, the interior of the gear, in particular the engagement area between the worm wheel 27 and the worm 21, is at least partially filled with a first lubricant, in particular lubricating oil, and sealed against the environment.

[0042] However, a second lubricant, in particular lubricating grease, can also be introduced into the bearing housing to lubricate the bearing 22.

[0043] This is because, on the side axially remote from the second shaft seal 25, a flange part 28 is fitted into the bearing bore of the bearing housing 2, in which a third shaft seal 23 is accommodated, which also seals towards the output shaft 3.

[0044] Also arranged within the bearing housing 2 is a clamping 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 it against a shaft collar of the output shaft 3.

[0045] Thus, the bearing tension can be adjusted using the clamping nut 24.

[0046] During gearbox production, after screwing the clamping nut 24 onto the output shaft 3 and adjusting the bearing tension of the bearing 22, the flange part 28 is fitted and secured to the bearing housing 2 with screws. The clamping nut 24 is thus radially surrounded by the flange part 28 and thus exposed to a second lubricant. This prevents or at least reduces corrosion.

[0047] The clamping nut 24 rotates with the output shaft and presses on the inner ring or one of the inner rings of the bearing 22.

[0048] The output shaft 3 is preferably designed as a hollow shaft. The first shaft seal 26 is preferably designed as a pair of shaft seals.

[0049] The second shaft sealing ring 25 is preferably also designed as a pair of shaft sealing rings.

[0050] The third shaft seal 23 is preferably also designed as a pair of shaft seals.

[0051] 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 distance from the axis of rotation 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. than the running surface of the third shaft sealing ring 25 on the output shaft 3.

[0052] What is important about the invention is that the second shaft seal 25 is not housed in the housing part of the gearbox, but in the bearing housing 2. Thus, the heat loss generated at the second shaft seal 25 is dissipated to the environment through the bearing housing 2.

[0053] A heat barrier can thus also be provided between the bearing housing 2 and the housing part 1, so that the housing part 1 only dissipates the heat of the first lubricant, i.e. the heat loss from the gear engagements, and the heat loss of the first bearing 20 as well as a portion of the first shaft sealing ring 26, which is accommodated in a flange 29 which is connected to the housing part 1.

[0054] The outer diameter of the bearing housing 2 increases monotonically with increasing axial distance from the worm gear 27 and / or the first shaft seal 26. This enables improved heat dissipation to the environment. This is because the bearing housing 2 has a radial wall thickness that increases monotonically with increasing distance from the worm gear 27, at least in the area covered by the bearing 22 in the axial direction.

[0055] The axial direction is always aligned parallel to the rotational axis of the output shaft 3. The radial direction and the circumferential direction are each related to the rotational axis of the output shaft 3. The high thermal capacity allows for the absorption of temperature peaks. In further embodiments according to the invention, several blind holes are formed in the bearing housing 2, which are directed radially or at an angle such that the radial distance between the blind holes increases with increasing axial distance from the first bearing 20. These blind holes thus interrupt the bearing seat of the bearing 22.

[0056] The blind holes are spaced apart from each other in the circumferential direction, in particular evenly spaced.

[0057] Preferably, the bore axes of the blind holes form an angle of between 20° and 60° to the rotational axis of the output shaft 3. Thus, the bearing housing 2 has less mass and yet a high level of rigidity, so that even with high transverse forces introduced into the output shaft 3 on the load side, the spatial orientation of the output shaft remains essentially constant. In addition, the blind holes are at least partially filled with the second lubricant, so that corrosion is reduced or at least minimized. Alternatively, the blind holes can be filled with a thermally conductive paste, in particular one that hardens after filling and does not chemically bond with the lubricant or dissolve in it. This thermally conductive paste can also be mixed with an adhesive, which creates a material-to-material connection between the outer ring or between the outer rings of the bearing 22 and the bearing housing 2.Thus, the outer ring of the bearing 22 is secured against rotation relative to the bearing housing 2.

[0058] The blind holes thus also function as lubricant reservoirs, as the outer rings accommodated in the bearing seat do not completely seal the openings of the blind holes.

[0059] In further embodiments according to the invention, a different angular gear stage is used instead of the worm gear stage, in particular a bevel gear stage, in which the worm 21 is replaced by a bevel pinion and the worm gear 27 by a bevel gear. List of reference symbols

[0060] 1 Housing part 2 Bearing housing

[0061] 3 drifting shaft

[0062] 4 gearbox covers

[0063] 21 Worm gear

[0064] 22 Bearing, especially double-row bearing 23 Shaft seal

[0065] 24 clamping nut

[0066] 25 Shaft seal

[0067] 26 Shaft seal

[0068] 27 Worm wheel 28 Flange part

[0069] 29 Flange

Claims

Patent claims:

1. Gearbox with a housing part and a bearing housing connected to the housing part, wherein an output shaft of the gearbox is rotatably mounted by means of a first bearing which is received in the housing part, in particular wherein an outer ring of the first bearing is received in the housing part, in particular wherein the inner ring of the first bearing is placed on the output shaft, characterized in that the output shaft of the gearbox is rotatably mounted by means of a second bearing which is received in the bearing housing, in particular wherein an outer ring of the second bearing is received on a bearing seat formed on the bearing housing, in particular wherein the inner ring of the second bearing is placed on the output shaft, in particular wherein the second bearing is designed as a double-row angular contact bearing, in particular an angular contact tapered roller bearing or angular contact cylindrical roller bearing, in an X arrangement.

2. Gearbox with a housing part and a bearing housing connected to the housing part, wherein an output shaft of the gearbox is rotatably mounted by means of a first bearing which is received in the housing part, wherein an outer ring of the first bearing is received in the housing part, wherein the inner ring of the first bearing is placed on the output shaft, wherein the output shaft of the gearbox is rotatably mounted by means of a second bearing which is received in the bearing housing, wherein an outer ring of the second bearing is received on a bearing seat formed on the bearing housing, wherein the inner ring of the second bearing is placed on the output shaft, wherein the second bearing is designed as a double-row angular contact bearing, in particular an angular contact tapered roller bearing or angular contact cylindrical roller bearing, in an X arrangement.

3. Gearbox according to claim 1, characterized in that a first shaft sealing ring is accommodated in a flange connected to the housing part, which seals off the output shaft, in particular the sealing lip of which runs on a running surface of the output shaft and / or bears against it, wherein the flange is arranged on the side of the housing part axially facing away from the bearing housing, in particular wherein the flange is connected in a sealed manner to the housing part by means of an intermediate seal, in particular a flat seal.

4. Gearbox according to one of the preceding claims, characterized in that a second shaft sealing ring is accommodated in the bearing housing, which seals towards the output shaft, in particular whose sealing lip runs on a running surface of the output shaft and / or bears against it.

5. Gearbox according to one of the preceding claims, characterized in that the bearing housing is sealed to the housing part by means of a further seal, in particular a flat seal, arranged between the bearing housing and the housing part.

6. Gearbox according to one of the preceding claims, 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, wherein a third shaft sealing ring is accommodated in the flange part, which seals towards the output shaft, in particular whose sealing lip runs on a running surface of the output shaft and / or bears against it.

7. Gearbox according to one of the preceding claims, characterized in that the output shaft has an external thread area onto which a clamping nut is screwed with its internal thread, which preloads the second bearing, in particular in that the clamping nut presses an inner ring of the second bearing towards a shaft collar of the output shaft.

8. Gearbox according to one of the preceding claims, characterized in that the area covered by the clamping ring in the axial direction is encompassed by the area covered by the flange part in the axial direction.

9. Gearbox according to one of the preceding claims, characterized in that an angular gear stage is arranged within the housing part, which is lubricated by a first lubricant, in particular lubricating oil, wherein a second lubricant, in particular lubricating grease, is arranged within the bearing housing.

10. Transmission according to one of the preceding claims, characterized in that the housing part has an opening which is closed and / or covered by a transmission cover.

11. Gearbox according to one of the preceding claims, characterized in that a wheel, in particular a bevel gear or a worm gear of the angular gear stage is connected in a rotationally fixed manner to the output shaft and is in engagement with a bevel pinion or with a worm.

12. Gearbox according to one of the preceding claims, characterized in that the outer diameter of the bearing housing, in particular the outer diameter of the bearing housing relative to the axis of rotation of the output shaft, increases monotonically with increasing axial distance from the first bearing.

13. Gearbox according to one of the preceding claims, characterized in that the radial wall thickness of the bearing housing, in particular the radial wall thickness of the bearing housing related to the axis of rotation of the output shaft, increases monotonically with increasing axial distance from the first bearing.

14. Gearbox according to one of the preceding claims, characterized in that radially directed blind holes are made in the bearing housing, in particular in the bearing seat of the second bearing, in particular wherein the blind holes open into the space surrounded by the bearing flange and at least partially filled with the second lubricant, in particular wherein the respective mouth opening is covered by an outer ring of the bearing, in particular wherein the blind holes are evenly spaced from one another in the circumferential direction and / or wherein the blind holes are all arranged at the same axial position and / or wherein the blind holes all have the same angle to the axis of rotation of the output shaft, in particular 90°.

15. Gearbox according to one of claims 1 to 13, characterized in that blind holes are introduced into the bearing housing, in particular into the bearing seat of the second bearing, wherein the hole axes of the blind holes each have an angle between 20° and 60° to the axis of rotation of the output shaft, in particular wherein the blind holes open into the space surrounded by the bearing flange and at least partially filled with the second lubricant, in particular wherein the respective mouth opening is covered by an outer ring of the bearing, in particular wherein the blind holes are evenly spaced from one another in the circumferential direction and / or wherein the blind holes are all arranged at the same axial position and / or wherein the blind holes all have the same angle to the axis of rotation of the output shaft, in particular 45°.

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