CN212564320U - Speed reducer with shaft and housing part - Google Patents
Speed reducer with shaft and housing part Download PDFInfo
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- CN212564320U CN212564320U CN202021251470.2U CN202021251470U CN212564320U CN 212564320 U CN212564320 U CN 212564320U CN 202021251470 U CN202021251470 U CN 202021251470U CN 212564320 U CN212564320 U CN 212564320U
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- shaft
- sealing ring
- radial
- oil
- bearing
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Abstract
The utility model relates to a reduction gear with axle and housing part. A bearing for rotatably supporting the shaft is received in the housing part, the flange part is connected to the housing part, at least one shaft sealing ring is received in the flange part, the shaft sealing ring seals the flange part against the shaft, a sealing ring is arranged axially between the shaft sealing ring and the bearing, such that a first spatial region is formed between the sealing ring and the rolling elements of the bearing, which first spatial region can be at least partially filled with oil for supplying the bearing or the rolling elements of the bearing with lubricating oil, such that a second spatial region is formed between the sealing ring and the shaft sealing ring, which second spatial region can be at least partially filled with oil for supplying the shaft sealing ring with lubricating oil, which second spatial region opens into a first radial bore of the flange part via a first passage, which first spatial region opens into the first radial bore.
Description
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
It is therefore an object of the present invention to provide a reduction gear having a longer service life.
In the case of a reduction gear having a shaft and a housing part, an important feature of the invention is that a bearing, in particular a bearing for rotatably supporting the shaft, is accommodated in the housing part,
the flange member is connected to the housing member,
at least one shaft seal ring is received in the flange member,
the shaft seal ring seals the flange member toward the shaft,
a sealing ring is arranged between the shaft seal ring and the bearing along the axial direction,
such that a first spatial region is formed between the sealing ring and the bearing, in particular between the sealing ring and the rolling elements of the bearing, which first spatial region can be at least partially filled with oil, in particular for supplying the bearing or the rolling elements of the bearing with lubricating oil,
such that a second spatial region is formed between the sealing ring and the shaft sealing ring, which second spatial region can be at least partially filled with oil, in particular for supplying the shaft sealing ring with lubricating oil,
the second spatial region opens into the first radial bore of the flange part via a passage,
the first spatial region opens into the first radial bore.
The advantage of this is that the supplied oil flow is divided into a first portion which is guided out of the first radial bore into the first space region and there supplies the bearing with lubricating oil, in particular the rolling bodies of the bearing and dissipates their heat, without the shaft sealing ring being loaded with such heat which is absorbed by the bearing in the oil flow. Since the second part of the conveyed oil flow is led to the shaft sealing ring, this is supplied with cooled oil.
The shaft sealing rings can be designed as shaft sealing ring pairs. In this case, the two shaft sealing rings are arranged axially next to one another and are in contact with one another. Preferably, the part of the shaft sealing ring of the pair of shaft sealing rings facing the sealing ring, which part flows through the first passage, is supplied with oil flow, and the other shaft sealing ring, i.e. the shaft sealing ring of the pair of shaft sealing rings, which is arranged further away from the sealing ring, is lubricated with grease.
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. It is thus possible to realize the supply of lubricating oil to the shaft seal ring and the bearing.
In an advantageous embodiment, a first part of the oil flow conveyed by the conveying device flows into the first space region through the radial bores and a second part of the oil flow conveyed by the conveying device flows into the second space region through the radial bores. The advantage is that the first portion is at least ten times as large as the second portion, so that at least a major part of the heat loss of the bearing can be removed by the oil and at least a major part of the heat loss of the shaft sealing ring can be removed by the oil, which is also supplied with oil, in particular so that the oil film is not interrupted in the region of the sealing lips of the shaft sealing ring and in the region of the shaft.
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 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, the lubricating oil of the gear unit can be supplied to the first radial bores. This has the advantage that the oil supply can be established simply.
In an advantageous embodiment, the passage is designed as a radial bore which has a smaller diameter than the first radial bore. This has the advantage that the oil flow to the shaft sealing ring is smaller than to the bearing.
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 the load of the drive shaft can introduce lateral forces that can be absorbed by the bearings.
In an advantageous embodiment, the flange part is formed integrally, in particular in one piece,
in particular
Wherein the flange part and the sealing ring are made of plastic as a plastic injection-molded part,
-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 formed 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, wherein the shaft sealing rings are of course preferably designed as a pair of shaft sealing rings, so that sufficient tightness is present in the case of high transverse forces. In the case of designs made of metal, it is important that a sufficiently large gap exists between the sealing ring and the shaft, so that the shaft does not come into contact with the sealing ring in the event of transverse forces. 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 channel opens into the second radial bore,
in particular wherein the diameter of the first channel is smaller than the diameter of the second channel. This has the advantage that the return flow is ensured without significant resistance.
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 delivered can flow back into the oil sump of the retarder 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 delivery device is conveyed from the oil sump or the subsequent oil delivery 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 shaft seal ring facing away from the sealing ring in the axial direction. Its advantage is that the dust-proof of shaft sealing ring can be realized. Only a narrow gap remains between the cover plate and the shaft.
In an advantageous embodiment, the radial length region covered by the cover plate comprises a radial length region covered by the shaft seal ring, which radial length region, in addition to the radial length region covered by the sealing lip of the shaft seal ring,
in particular, the sealing lip of the shaft seal contacts the finished running surface of the shaft, the cover plate being spaced apart from the shaft. The advantage of this is that the cover covers the shaft seal, except for the 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 low thermal loading capacity can also be used with the cooled oil.
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 a high tightness to the second space region can be achieved with respect to the first space region having a higher temperature level.
In an advantageous embodiment, the radial length area covered by the sealing ring comprises the radial length area 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. This has the advantage that the sealing ring adequately shields the second spatial region 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.
Drawings
The invention is described in detail below with reference to the schematic drawings:
fig. 1 shows a cross section of a gear reducer according to the invention with a bearing arrangement.
Fig. 2 shows an oblique view of a cut-away region of the retarder.
List of reference numerals:
1 housing part
2 Flange part
3 first radial hole
4 sealing ring
5 shaft seal ring
6-shaft, in particular hollow shaft
7 second spatial region for lubricating oil
8 first axial hole
9 bearing, in particular radial thrust bearing
10 channel
11 cover plate
12 second radial hole
13 second axial hole
14 first spatial region
Detailed Description
As shown in the figures, 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 the following oil levels are present in the inner space: this oil level does not reach or only partially reaches the rolling bodies of the bearing 9, in particular only reaches the innermost 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 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 a first empty space 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 and the empty first spatial region 14.
The free space region 14 directly adjoins the bearing 9 in the axial direction 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 is mounted on a fixed ring arranged on the shaft 6 or in an alternative design on a step of the shaft 6. The outer ring is likewise axially retained by the ring part or by the flange part 2 itself.
The radial spacing is referred to the axis of rotation of the shaft 6, 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.
Two shaft sealing rings 4 are received in the flange part 2, which are arranged axially next to one another, in particular in contact with one another, the sealing lips of which are moved over, in particular in contact with, a finished, in particular polished, running surface designed on the surface of the shaft.
The shaft sealing ring 4 is arranged on the side of the sealing ring 4 facing away from the bearing 9 in the axial direction.
The sealing ring 4 reduces or prevents the oil flow from the second spatial region 7 to the first spatial region 14.
Axially between the flange part 2 and the seal 4, a radially extending channel 10 is provided, which is guided from the first spatial region or from the first radial bore 3 adjoining the first spatial region to the second spatial region 7 and thus conveys lubricating oil which has not yet been heated by the bearing 9 at least to at least one of the shaft sealing rings 5. Thus preventing wear of the gland seal 5.
The sealing ring 4 is also arranged axially between the bearing 9 and the shaft sealing ring 5 and thus separates the oil in the region of the bearing 9 from the oil in the region of the shaft sealing ring 5, wherein the oil in the region of the bearing 9 has a higher temperature than the oil in the region of the shaft sealing ring 5.
The cover plate 11 is connected to the flange part 2, in particular by means of screws, the threaded region of which is screwed into the threaded bore of the flange part 2 and the head of which presses the cover plate 11 onto the flange part 2.
The cover plate 11 covers the shaft seal 5 towards the surroundings. In particular, the radial length area covered by the cover plate 11 comprises the radial length area covered by the shaft seal ring 5, except for the radial length area covered by the sealing lip of the shaft seal ring 5. Because the sealing lip contacts the work surface being finished on the shaft 6; while the cover plate 11 is spaced from the shaft 6.
The cover plate 1 serves as a protection against contamination of the shaft seal 5 by dirt particles.
Preferably, the sealing ring 4 is received by the flange part 2 and is thus retained by the flange part. The sealing ring 4, in particular a sealing lip provided on the sealing ring 4, likewise contacts the shaft 6 or at least only has a spacing of less than 100 μm.
The strength of the oil flow flowing through the first radial bore 3 to the second space region 7 can be controlled by means of the diameter of the channel 10. Since only a small amount of oil is required for lubricating the shaft sealing ring 5, a small diameter of the passage 10 is sufficient, in particular a diameter of less than two centimeters or less than one centimeter.
The channel 10 is arranged as high as possible, that is to say as close as possible to the first axial bore 8.
In the lower region of the sealing ring 4, that is to say at a position which is as far away as possible from the first axial bore 8, a further channel is designed on the flange part 2 as a return for oil which 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 oil which 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. Only those oil portions which flow past the rolling bodies of the bearing 9 absorb more heat than those oil portions which flow past the shaft sealing ring 5.
The cover plate 11, the flange part 2 and the housing part 1 are made of metal, in particular steel.
For receiving the shaft sealing ring 5, the flange part has a corresponding support, which is finished, in particular ground. A shaft sealing ring 5 received on the support seals the flange part 2 with respect to the shaft 6.
The sealing lip of the shaft seal is thus displaced on the running surface of the shaft, in particular wherein the sealing lip of the shaft seal contacts the running surface of the shaft.
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, the inner ring of which is mounted relative to 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 integrally, with the sealing ring 4. Preferably, to produce such a flange component 2 with an integrated sealing ring 4, an additive manufacturing method is carried out, in particular using a 3D printer. Preferably, the flange part 2 and the integrated sealing ring 4 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 sealing ring 4 can also be made of metal. Here, a sufficiently large gap exists between the sealing ring 4 and the shaft 6 in order to prevent the shaft from contacting the sealing ring 4 in the event of transverse forces.
Embodiments of the metal can also be produced as additive, wherein correspondingly formed holes can be provided instead of openings.
Claims (15)
1. A speed reducer having a shaft and a housing member,
a bearing for rotatably supporting the shaft is received in the housing part,
it is characterized in that the preparation method is characterized in that,
the flange member is connected to the housing member,
at least one shaft seal ring is received in the flange member,
the shaft seal ring seals the flange member toward the shaft,
a sealing ring is arranged between the shaft seal ring and the bearing along the axial direction,
such that a first spatial region is formed between the sealing ring and the rolling elements of the bearing, which first spatial region can be at least partially filled with oil for supplying the bearing or the rolling elements of the bearing with lubricating oil,
such that a second spatial region is formed between the sealing ring and the shaft seal ring, which second spatial region can be at least partially filled with oil for supplying the shaft seal ring with lubricating oil,
the second spatial region opens into a first radial bore of the flange part via a first passage,
the first spatial region opens into the first radial bore.
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 oil flow delivered by the oil delivery device flows into the first radial hole.
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 first part of the oil flow delivered by the oil delivery device flows through the first radial bores into the first space region,
a second part of the oil flow delivered by the oil delivery device flows into the second spatial region through the first radial bores.
4. 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 delivery device has an oil pump driven by the motor or the shaft of the speed reducer and/or a collection unit for collecting oil sprayed to a high place in the rotational motion of the toothed member of the speed reducer.
5. 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,
a first axial bore through the housing part opens into the first radial bore,
so that the lubricating oil of the speed reducer can be delivered to the first radial holes.
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 first channel is designed as a radial bore, which has a smaller diameter than the first radial bore.
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 bearing is a radial thrust bearing, the shaft is designed as a hollow shaft,
the shaft is the output shaft of the reducer, wherein the shaft is the largest diameter shaft of all the shafts of the reducer.
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 flange part is formed integrally with the sealing ring,
wherein the flange part and the sealing ring are made of plastic as a plastic injection-molded part,
-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 a second radial bore is provided, the first radial bore and the second radial bore being designed as a formed or additively formed channel and not being manufactured by tapping.
9. 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,
a second radial hole is arranged on the outer wall of the sleeve,
the second passage opens into the second radial bore,
the diameter of the first passage is smaller than the diameter of the second passage.
10. 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,
a second radial bore of the flange part is provided, which opens into a second axial bore running through the housing part, which opens into the interior of the gear unit.
11. 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 cover plate is connected with the flange part,
the cover plate is arranged on the side of the shaft seal ring facing away from the sealing ring in the axial direction.
12. A decelerator having a shaft and a housing member according to claim 11,
it is characterized in that the preparation method is characterized in that,
the radial length area covered by the cover plate comprises the radial length area covered by the shaft seal ring, except for the radial length area covered by the sealing lip of the shaft seal ring,
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.
13. A decelerator having a shaft and a housing member according to claim 9,
it is characterized in that the preparation method is characterized in that,
the sealing ring is made of plastic and/or rubber,
the sealing ring is in full contact with the flange part in the circumferential direction, except for a circumferential angular area covered by the first and second channels.
14. 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 radial length area covered by the sealing ring comprises the radial length area covered by the shaft sealing ring,
the radial length area covered by the sealing ring overlaps the radial length area covered by the shaft sealing ring.
15. A decelerator having a shaft and a housing member according to claim 9,
it is characterized in that the preparation method is characterized in that,
the first radial hole is sealed towards the surroundings by means of a plug inserted at least partially into the first radial hole,
the second radial bore is sealed towards the ambient environment by means of a plug inserted at least partially into the second radial bore.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202021251470.2U CN212564320U (en) | 2020-07-01 | 2020-07-01 | Speed reducer with shaft and housing part |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202021251470.2U CN212564320U (en) | 2020-07-01 | 2020-07-01 | Speed reducer with shaft and housing part |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN212564320U true CN212564320U (en) | 2021-02-19 |
Family
ID=74613893
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202021251470.2U Active CN212564320U (en) | 2020-07-01 | 2020-07-01 | Speed reducer with shaft and housing part |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN212564320U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113958691A (en) * | 2020-07-01 | 2022-01-21 | Sew-工业减速机(天津)有限公司 | Speed reducer with shaft and housing part |
-
2020
- 2020-07-01 CN CN202021251470.2U patent/CN212564320U/en active Active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113958691A (en) * | 2020-07-01 | 2022-01-21 | Sew-工业减速机(天津)有限公司 | Speed reducer with shaft and housing part |
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