Gear unit with a housing part with a driving shaft
The gearbox integrates a cooling pipe system within the input-side flange area using concentric annular grooves and semicircular tubes to efficiently dissipate heat from the rapidly rotating input shaft, addressing thermal power losses and improving heat transfer efficiency.
Patent Information
- Authority / Receiving Office
- WO · WO
- Patent Type
- Applications
- Current Assignee / Owner
- SEW EURODRIVE GMBH & CO KG
- Filing Date
- 2025-11-17
- Publication Date
- 2026-07-02
AI Technical Summary
Existing gearboxes experience thermal power losses due to inefficient heat dissipation, particularly from the rapidly rotating input shaft, which generates high heat flow.
A compact gearbox design integrates a cooling pipe system within the input-side flange area, utilizing concentric annular grooves and semicircular ring tubes, with a cooling medium flowing through these tubes to efficiently dissipate heat from the bearing arrangement and housing part.
The integrated cooling system effectively transfers heat from the gearbox components to the cooling medium, reducing thermal resistance and minimizing installation space, thereby enhancing heat dissipation and reducing thermal losses.
Smart Images
Figure EP2025083267_02072026_PF_FP_ABST
Abstract
Description
[0001] Gearbox with a housing part with an incoming shaft
[0002] Description:
[0003] The invention relates to a gearbox with a housing part with an input shaft.
[0004] It is known that gearboxes exhibit thermal power losses during operation.
[0005] From CN 1 19906 194 A, a gearbox is known as the closest state of the art.
[0006] A branch gearbox with a cooling jacket is known from DE 3331 038 A1.
[0007] A cooling system for an electric motor is known from US patent 2010 / 0295391 A1.
[0008] A cooling flange is known from CN 2 14743235 U.
[0009] A mechatronically integrated module is known from JP 2013 - 172564 A.
[0010] The invention is therefore based on the objective of further developing a compact gearbox.
[0011] According to the invention, the problem is solved in the transmission according to the features specified in claim 1.
[0012] Important features of the invention for the gearbox with a housing part with a driving shaft are that a flange area is formed on the drive side of the housing part, in which annular grooves arranged concentrically to each other and concentrically to the axis of rotation of the driving shaft are machined,
[0013] wherein semicircular ring tubes are accommodated in the ring grooves.
[0014] An advantage of this design is the compact gearbox, as the cooling pipe system is integrated within the gearbox and requires little installation space. In particular, the cooling pipe system is integrated into the input-side flange area. This is because the rapidly rotating input shaft generates a high temperature and therefore a high heat flow.
[0015] ISI \ EIDOPAT 17.11.2025, efficient heat dissipation is achievable according to the invention. This is because the cooling pipe system is arranged as close as possible to the bearing arrangement for the driving shaft, which acts as a heat source.
[0016] In an advantageous embodiment, connecting parts and a connection part are arranged on the flange area of the housing part.
[0017] in particular wherein the connecting parts and the connecting part are each pressed against the flange area by means of screws screwed into threaded holes in the flange area,
[0018] In particular, the screws protrude through the connecting parts and the terminal part. It is advantageous that fastening to the input-side end face is possible.
[0019] In an advantageous embodiment, each of the connecting parts connects a semicircular annular tube to a neighboring annular tube arranged radially inside it in a first circumferential half. It is advantageous that the cooling medium flow first meanders through the semicircular annular tubes from radially outside to radially inside in the first circumferential half, and then meanders through the semicircular annular tubes from radially inside to radially outside in the remaining circumferential half.
[0020] In an advantageous embodiment, each of the connecting parts connects a semicircular annular tube in the other circumferential half to a neighboring annular tube arranged radially inside that annular tube. It is advantageous that the cooling medium flow first meanders through the semicircular annular tubes from radially outside to radially inside in the first circumferential half, and then meanders through the semicircular annular tubes from radially inside to radially outside in the remaining circumferential half.
[0021] In an advantageous embodiment, the connecting part connects a first channel formed in the housing part to a first opening of a first, radially outermost, semi-annular annular tube. The advantage here is that a simple and cost-effective connection can be achieved. In an advantageous embodiment, the connecting part connects a second channel formed in the housing part to a first opening of a second, radially outermost, semi-annular annular tube. The advantage here is that a simple and cost-effective connection can be achieved. In an advantageous embodiment, the radially innermost annular tube is designed as a solid annular tube and is connected to the radially innermost connecting part. The advantage here is that a simple and cost-effective connection can be achieved.
[0022] In an advantageous embodiment, spacers are arranged radially between the ring tubes.
[0023] In particular, those that are pressed against the flange area by screws screwed into threaded holes in the flange area. An advantage of this method is that the spacing is easily ensured.
[0024] In a preferred design, the first channel leads to an inlet connection and the second channel to an outlet connection. The advantage here is that the inlet and outlet of the cooling medium are very compact, thus saving installation space. In particular, the cooling medium also flows directly through the housing component and thus absorbs heat directly from it.
[0025] In an advantageous embodiment, the first channel extends in the axial direction, in particular parallel to the axis of rotation of the driving shaft, and through the housing part, specifically projecting through the flange area that extends radially from the housing part. An advantage of this is that heat is transferred directly from the housing part into the cooling medium.
[0026] In an advantageous embodiment, the second channel extends axially, in particular parallel to the axis of rotation of the driving shaft, and projects through the housing part, especially through the flange area projecting radially from the housing part. An advantage of this is that heat is transferred directly from the housing part into the cooling medium.
[0027] In an advantageous embodiment, the flange area has a continuous bearing bore through which the driving shaft protrudes,
[0028] wherein a bearing of the driving shaft is received in the bearing bore. An advantage of this is that the inner ring of the bearing is mounted on the driving shaft and the outer ring of the bearing is received in the bearing bore. Thus, the heat loss from the bearing flows directly into the flange area. In an advantageous embodiment, each ring tube is designed as a lamellar ring tube.
[0029] in particular wherein continuous lamellae project radially from the tube in the circumferential direction and / or wherein the lamellae are evenly spaced apart from each other on the tube.
[0030] An advantage of this is that the lowest possible thermal resistance between the finned ring tube and the housing part can be achieved. Furthermore, the respective ring tube is preferably encased in a thermally conductive potting compound and provided in the respective ring groove.
[0031] In an advantageous embodiment, an annular gap through which a cooling medium flows is formed between the housing part and a cover plate. This annular gap radially surrounds a hollow cylindrical bearing receptacle formed on the housing part. An advantage of this design is that efficient heat dissipation from the housing part is achieved. In particular, the cover plate can be provided in the axial area covered by the bearing in the axial direction.
[0032] In an advantageous embodiment, projections are formed on the housing part, particularly on the bearing receptacle, which are spaced apart from one another in the circumferential direction, in particular uniformly spaced from one another, and project radially outwards from the bearing receptacle towards the cover plate, in particular projecting through the annular gap. It is advantageous that the projections make the cooling medium flow more turbulent and thus enable a lower thermal resistance.
[0033] In an advantageous embodiment, the cover plate rests on the raised sections. It is advantageous that the annular gap is located between the bearing receptacle of the housing part and the cover plate.
[0034] In an advantageous embodiment, the cover plate is bonded to the projections by a material bond, in particular by welding. The advantage here is that a secure and durable connection can be used. In an advantageous embodiment, the longest extension of each projection is formed and / or aligned in the direction transverse to the flow direction and / or in the axial direction, in particular parallel to the direction of rotation.
[0035] In particular, the flow direction, especially the main flow direction, of the cooling medium is essentially oriented circumferentially. It is advantageous that the protrusions are perpendicular to the flow direction and thus cause effective turbulence of the cooling medium flow.
[0036] In an advantageous embodiment, the axial width of the respective projection is smaller than the axial width of the annular gap. This is advantageous because the cooling medium flow still has sufficient clearance to flow circumferentially.
[0037] In an advantageous embodiment, the annular gap is limited and / or covered radially outwards by a cover plate.
[0038] In particular, the cover plate consists of flat areas with bending edges between them. An advantage of this design is that heat is radiated to the surroundings even through the thin cover plate, and the additional installation space required for the cooling system is extremely minimal. Specifically, only a radial allowance is necessary, equal to the radial width of the protrusions and the cover plate. However, the cover plate follows the protrusions, which all have the same radial width, and is therefore curved or made of flat individual surface pieces arranged at angles to each other.
[0039] In an advantageous embodiment, the annular gap in the circumferential angle region not covered by the cover plate is arranged in an annular groove section integrated into the housing part, which radially surrounds the bearing receptacle in this circumferential angle region. It is advantageous that the annular gap is limited radially outward either by a cover plate or by the housing part itself. A two-piece design of the cover plate is also included. Further advantages are set forth in the dependent claims. The invention is not limited to the combination of features in the claims. For those skilled in the art, further meaningful combinations of claims and / or individual claim features and / or features of the description and / or the figures will be apparent, in particular from the problem statement and / or the problem arising from a comparison with the prior art.
[0040] The invention will now be explained in more detail with reference to schematic illustrations:
[0041] Figure 1 shows a gear unit according to the invention in an oblique view.
[0042] Figure 2 shows the gearbox open on the input side.
[0043] Figure 3 shows an exploded, oblique view of a cooling pipe arrangement located on the input side of the gearbox.
[0044] Figure 4 shows an exploded view of an alternative or additional cooling arrangement of the gearbox.
[0045] Figure 5 shows the alternative or additional cooling arrangement of the gearbox in an oblique view.
[0046] As shown in the figures, the gearbox has a housing part 1 which provides a flange area 7 on the input side of the gearbox and which accommodates a bearing of the input shaft of the gearbox.
[0047] On its side facing away from the flange area 7, the housing part 1 is connected to a bearing flange 4, which accommodates a bearing of the driving shaft, in particular a hollow shaft.
[0048] Preferably, the gearbox is designed as a coaxial gearbox, in particular a planetary gearbox. As shown in Figure 2, the flange area 7 has concentrically arranged annular grooves 22.
[0049] A connecting part 20 and connecting parts 21 are arranged one behind the other in a radial direction. The connecting part 20 is arranged radially outside the connecting parts 21.
[0050] The ring grooves 22 accommodate semi-ring-shaped ring tubes 30, which are connected with their end regions viewed in the circumferential direction to a respective connecting part 21.
[0051] Each connecting part 21 connects a first of the semicircular ring tubes 30 with a second semicircular ring tube 30 arranged radially inside the first, which is arranged in the same circumferential angle range as the first.
[0052] In the remaining circumferential angle range i arranged outside this circumferential angle range, each connecting part 21 also connects a third of the semicircular ring tubes 30 with a fourth, radially inside the third semicircular ring tube 30, which is arranged in the same circumferential angle range as the third.
[0053] A supply connection 2 enables the supply of a cooling medium through a channel formed in the housing part 1 to the connection part 20.
[0054] The connecting part 20 is connected to the two radially outermost ring tubes 30, which are connected diametrically opposite the connecting part 20 to a first connecting part.
[0055] In this way, the cooling medium, in particular water or oil, flows through the radially outermost annular tube 30 in the first circumferential angle range and then successively through the further radially inner annular tubes with alternating flow directions, in particular circumferential or counter-circular, until the radially innermost annular tube 30, which is designed as a solid ring and thus returns the cooling medium from radially inner to radially outer through the semicircular annular tubes in the other circumferential angle range to the outermost semicircular annular tube 30, from where it is diverted by the connection part 20 through a channel formed in the housing part 1 to the outlet connection 3.
[0056] In summary, the cooling medium flows through the semi-annular ring tubes 30 in the first circumferential half, successively from the radial outside to the radial inside, until it reaches the essentially full-ring, radially innermost ring tube 30. From there, it flows through the other circumferential half, successively from the radial inside to the radial outside. This method of heat dissipation from the flange area 7 achieves efficient heat dissipation from the driving side. It is important to note that the bearing of the driving shaft and a shaft seal located next to this bearing act as two significant sources of heat loss.
[0057] The axial direction is aligned parallel to the axis of rotation of the driving shaft, and the radial direction is relative to this axis of rotation of the driving shaft. Similarly, the circumferential direction is relative to the axis of rotation of the rotor shaft.
[0058] As shown in Figure 4 and Figure 5, a further cooling arrangement is implemented on the housing part.
[0059] The cooling medium flows through an annular gap, on the radial inside of which radially directed protrusions 40 are arranged, which generate turbulence in the cooling medium and thus a more efficient heat transfer from the housing part to the cooling medium.
[0060] The elevations 40 are spaced apart from each other in the circumferential direction and are formed on a hollow cylindrical bearing receptacle, from which they each project in a radially outward direction.
[0061] A cover plate 41 defines the radial outer boundary of the annular gap. The cover plate 41 has circumferentially arranged regions, each with a bending edge between them. These regions are preferably flat or preferably have at least one flat area. The regions 41 and 41 have a non-zero angle to their nearest adjacent region and are therefore not parallel. The cover plate 41 rests on the projections 40 and thus defines and limits the space for the cooling medium. Preferably, the cover plate 41 is welded to the projections 40.
[0062] A supply connection 2 is arranged on the housing part, which is connected to the space for the cooling medium via a channel formed in the housing part 7.
[0063] An outlet connection 3 is arranged on the housing part, which is connected to the space for the cooling medium 3 via a channel formed in the housing part 7.
[0064] Thus, the heat dissipation of the gearbox via the two cooling arrangements is possible - either simultaneously or alternatively, as can be foreseen.
[0065] In the area not covered in the circumferential direction by the cover plate 41, the annular gap is realized as an annular groove of the housing part, with the radial outside of the hollow cylindrical bearing receptacle acting as the radial inside of the annular gap.
[0066] In further embodiments according to the invention, a plastic injection molded part is used instead of the cover plate 22 and is glued to the protrusions 40 instead of
[0067] welded. Reference list
[0068] 1 housing part
[0069] 2 Supply connection
[0070] 3. Outlet connection
[0071] 4 bearing flange
[0072] 5 Supply line connection
[0073] 6. Outlet connection
[0074] 7 Flange area
[0075] 20 Connection part
[0076] 21 Connecting part
[0077] 22 Ring groove
[0078] 30 ring tube
[0079] 31 spacers
[0080] 40 Survey
[0081] 41 Cover plate
Claims
Patent claims:
1. Gearbox with a housing part with an input shaft, characterized by the fact that a flange area is formed on the drive side of the housing part, in which annular grooves arranged concentrically to each other and concentrically to the axis of rotation of the driving shaft are machined, wherein semicircular ring tubes are received in the ring grooves.
2. Gearbox according to claim 1 , characterized by the fact that Connecting parts and a terminal part are arranged on the flange area of the housing part in particular wherein the connecting parts and the connecting part are each pressed against the flange area by means of screws screwed into threaded holes in the flange area, in particular where the screws protrude through the connecting parts and the connecting part.
3. Transmission according to any of the preceding claims, characterized by the fact that Each of the connecting parts connects a semicircular ring tube in a first circumferential half with a next adjacent ring tube arranged radially inside this ring tube. and / or that Each of the connecting parts connects a semicircular ring tube in the other circumferential half to a neighboring ring tube arranged radially inside this ring tube.
4. Transmission according to any of the preceding claims, characterized by the fact that the connecting part connects a first channel formed in the housing part with a first opening of a first, radially outermost, semi-ring-shaped annular tube.
5. Transmission according to any of the preceding claims, characterized by the fact that The connecting part connects a second channel formed in the housing part with a first opening of a second, radially outermost, semi-annular ring tube.- 15 - 6. Transmission according to any of the preceding claims, characterized by the fact that The radially innermost ring tube is designed as a solid ring tube and is connected to the radially innermost connecting part.
7. Gearbox according to any of the preceding claims, characterized by the fact that Spacers are arranged radially between the ring tubes. in particular those which are pressed against the flange area by screws screwed into threaded holes in the flange area.
8. Gearbox according to any of the preceding claims, characterized by the fact that the first channel leads into an inlet connection (5) and the second channel into an outlet connection (6).
9. Gearbox according to any of the preceding claims, characterized by the fact that the first channel extends in the axial direction, in particular parallel to the axis of rotation of the driving shaft, and projects through the housing part, in particular through the flange area projecting radially from the housing part, and / or that the second channel extends in the axial direction, in particular parallel to the axis of rotation of the driving shaft, and projects through the housing part, in particular through the flange area projecting radially from the housing part.- 16- 10. Gearbox according to any of the preceding claims, characterized by the fact that the flange area has a continuous bearing bore through which the driving shaft protrudes, wherein a bearing of the driving shaft is received in the bearing bore.
11. Gearbox according to any of the preceding claims, characterized by the fact that Each ring tube is designed as a lamellar ring tube, in particular wherein continuous lamellae project radially from the tube in the circumferential direction and / or wherein the lamellae are evenly spaced apart from each other on the tube.
12. Gearbox according to any of the preceding claims, characterized by the fact that An annular gap, through which the cooling medium flows, is formed between the housing part and a cover plate, radially surrounding a hollow cylindrical bearing receptacle formed on the housing part.- 17- 13. Gearbox according to any of the preceding claims, characterized by the fact that on the housing part, in particular on the bearing receptacle, projections are formed which are spaced apart from each other in the circumferential direction, in particular are spaced evenly apart from each other, and project radially outwards from the bearing receptacle towards the cover plate, in particular projecting through the annular gap, and / or that the cover plate rests on the raised areas and / or that the cover plate is bonded to the raised areas by a material connection, in particular by welding.
14. Gearbox according to any of the preceding claims, characterized by the fact that the longest extent of the respective elevation is present in a direction transverse to the flow direction and / or in an axial direction, in particular parallel to the direction of rotation, in particular wherein the flow direction, especially the main flow direction, of the cooling medium is essentially oriented circumferentially.- 18- 15. Gearbox according to any of the preceding claims, characterized by the fact that the axial width of the respective elevation is smaller than the axial width of the annular gap, and / or that the annular gap is limited and / or covered radially outwards by a cover plate, in particular wherein the cover plate consists of flat areas between which bending edges are arranged, and / or that The annular gap in the circumferential angle range which is not covered by the cover plate is arranged in an annular groove section incorporated into the housing part, which radially surrounds the bearing receptacle in the circumferential angle range.