Speed reducer
By constructing an annular gap and setting a protrusion in the reducer to promote turbulence of the cooling medium, and integrating a cooling pipe system, the problem of heat loss in the reducer is solved, and efficient heat dissipation effect and compact design are achieved.
Patent Information
- Application Number
- CN202423279071.8
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2024-12-27
- Publication Date
- 2025-10-03
- Estimated Expiration
- 2034-12-27
AI Technical Summary
The reducer has the problem of heat loss power during operation, and the heat dissipation efficiency needs to be improved.
An annular gap is constructed between the housing and the cover of the reducer, and heat is dissipated by the cooling medium flowing through the gap. A protrusion is provided on the housing to promote the flow of turbulent medium. Combined with the cooling pipe system integrated in the input side flange area, efficient heat dissipation is achieved.
Through the improved heat dissipation structure, the reducer can effectively reduce thermal resistance, achieve a compact design and improve heat dissipation efficiency, especially by directly cooling the high-temperature heat sources of the input bearing and sealing ring.
Smart Images
Figure CN223411439U_ABST
Abstract
Description
Technical Field
[0001] The utility model relates to a reducer, which comprises a housing and an input shaft. Background Art
[0002] It is known that retarder devices have thermal power losses during operation. Utility Model Content
[0003] Therefore, the object of the present invention is to improve a reducer in a compact manner.
[0004] The important feature of the present invention is that the reducer is provided with a housing part and an input shaft, wherein an annular gap through which a coolant flows is formed between a cover plate of the reducer and the housing part, in particular a bearing receptacle formed annularly, in particular a hollow-cylindrical, on the housing part, and the annular gap surrounds the hollow-cylindrical bearing receptacle formed on the housing part in the circumferential direction.
[0005] In particular, the bearing of the input shaft is received in the bearing receiving portion,
[0006] In particular, the bearing receptacle is a hollow-cylindrical region of the housing part.
[0007] The advantage here is that effective heat dissipation of the housing part can be achieved. In particular, the cover part can be arranged in an axial region covered by the bearing in the axial direction.
[0008] In one advantageous embodiment, projections are formed on the housing part, in particular on the bearing receptacle, which are spaced apart from one another in the circumferential direction, in particular uniformly spaced apart from one another, and project radially outward from the bearing receptacle toward the cover plate, in particular through the annular gap. The advantage here is that the projections make the coolant flow more turbulent and thus enable a lower thermal resistance to be achieved.
[0009] In an advantageous embodiment, the cover plate rests on the projection. Advantageously, the annular gap is arranged between the bearing receptacle of the housing part and the cover part.
[0010] In an advantageous embodiment, the cover is connected to the projection in a material-locking manner, in particular by welding. The advantage here is that a reliable and load-bearing connection can be used.
[0011] In an advantageous embodiment, the longest dimension of the respective projection is formed and / or oriented transversely to the flow direction and / or in the axial direction, in particular parallel to the direction of rotation.
[0012] In particular, the flow direction, in particular the main flow direction, of the coolant is oriented substantially in the circumferential direction. Advantageously, these projections are transverse to the flow direction and thus cause effective eddy currents in the coolant flow.
[0013] In an advantageous embodiment, the axial width of the respective projection is smaller than the axial width of the annular gap. This has the advantage that the coolant flow still has sufficient free space to flow in the circumferential direction.
[0014] In an advantageous embodiment, the annular gap is delimited and / or covered radially outwardly by a cover plate.
[0015] In particular, the cover plate consists of flat areas with folds arranged between them. This has the advantage that, even with a thin cover plate, heat is radiated to the environment, and the additional installation space required for the cooling system can be kept very small. In particular, only a radial machining allowance is required, which is equal to the radial width of the projection and the cover plate. However, the cover plate follows the projection, which has the same radial width, and is therefore designed to be curved or to consist of individual flat surfaces arranged at an angle to one another.
[0016] In one advantageous embodiment, the annular gap is arranged within the circumferential angular range not covered by the cover plate in an annular groove section formed in the housing part and circumferentially surrounding the bearing receptacle within this circumferential angular range. Advantageously, the annular gap is radially delimited to the outside by either the cover plate or the housing part itself. This also encompasses a two-part embodiment of the cover plate.
[0017] In an advantageous embodiment, a flange region is formed on the housing part on the input side, in which annular grooves are formed which are arranged concentrically with respect to one another and with respect to the axis of rotation of the input shaft.
[0018] In this case, a semicircular or semi-annular annular tube is received in the annular groove.
[0019] This has the advantage of enabling a compact design of the reducer, as the cooling pipe system is integrated into the reducer and requires very little installation space. In particular, the cooling pipe system is designed to be integrated into the flange area on the input side. Because the rapidly rotating input shaft generates high temperatures and, therefore, high heat flows, the present invention enables efficient heat dissipation. This is because the cooling pipe system is arranged as close as possible to the bearing assembly for the input shaft, which acts as a heat source.
[0020] In an advantageous embodiment, an interface component and a plurality of connecting elements are arranged on the flange region of the housing part.
[0021] In particular, the connecting piece and the interface part are each pressed against the flange area by means of screws which are screwed into threaded holes in the flange area.
[0022] Particularly wherein, the screw member passes through the connecting piece and the interface component. Advantage is that, can be fixed on the end face of the input side.
[0023] In an advantageous embodiment, each of the connecting elements connects the semicircular annular tube in the first half of the circumference to an adjacent annular tube arranged radially inward relative to the semicircular tube. This has the advantage that the coolant flow first flows in a meandering manner from the radial outside to the radial inside through the semicircular annular tube in the first half of the circumference and then flows in a meandering manner from the radial inside to the radial outside through the semicircular annular tube in the remaining half of the circumference.
[0024] In an advantageous embodiment, each of the connecting elements connects the semicircular annular tube in the other half of the circumference to an adjacent annular tube that is arranged radially inward relative to the semicircular tube. This has the advantage that the coolant flow first flows in a meandering manner from the radial outside to the radial inside through the semicircular annular tube in the first half of the circumference and then in a meandering manner from the radial inside to the radial outside through the semicircular annular tube in the remaining half of the circumference.
[0025] In an advantageous embodiment, the connection element connects the first channel formed in the housing part to the radially outermost, first opening of the semi-annular first annular tube. Advantageously, a simple, cost-effective connection can be achieved.
[0026] In an advantageous embodiment, the interface component connects the second channel formed in the housing part to the radially outermost, first opening of the semi-annular second annular tube. Advantageously, a simple, cost-effective connection can be achieved.
[0027] In an advantageous embodiment, the radially innermost annular tube is configured as a complete annular tube and is connected to the radially innermost connecting piece. This has the advantage that a simple, cost-effective connection can be achieved.
[0028] In an advantageous embodiment, spacers are arranged radially between the annular tubes.
[0029] Particularly, the spacer is pressed against the flange area using a screw threaded into the threaded hole in the flange area. Advantageously, spacing is ensured in a simple manner.
[0030] In one advantageous embodiment, the first channel opens into the inlet connection, and the second channel opens into the outlet connection. This has the advantage that the supply and discharge of the coolant are very compact, i.e., space-saving. In particular, the coolant also flows directly through the housing element, thus absorbing heat directly from the housing element.
[0031] In an advantageous embodiment, the first channel extends in an axial direction, in particular parallel to the rotation axis of the input shaft, and passes through the housing part, in particular through a radially protruding flange region on the housing part. This has the advantage that heat is transferred directly from the housing part to the coolant.
[0032] In an advantageous embodiment, the second channel extends in an axial direction, in particular parallel to the rotation axis of the input shaft, and passes through the housing part, in particular through a radially protruding flange region on the housing part. This has the advantage that heat is transferred directly from the housing part to the coolant.
[0033] In an advantageous embodiment, the flange region has a continuous bearing hole through which the input shaft passes.
[0034] The input shaft bearing is housed in the bearing bore. This has the advantage that the inner ring of the bearing is fitted onto the input shaft, while the outer ring of the bearing is housed in the bearing bore. Consequently, heat loss from the bearing flows directly into the flange area.
[0035] In an advantageous embodiment, each ring tube is designed as a laminar ring tube.
[0036] In particular, the lamellae protrude radially from the annular tube uninterrupted in the circumferential direction and / or the lamellae are uniformly spaced apart from one another on the annular tube. This has the advantage that the lowest possible thermal resistance can be achieved between the lamellae annular tube and the housing element. Furthermore, the respective annular tube is preferably encapsulated in the respective annular groove using a heat-conducting potting compound.
[0037] Further sensible combinations of features of the description and / or of the drawings will appear to a person skilled in the art, in particular arising from the objectives proposed and / or from a comparison with the prior art. BRIEF DESCRIPTION OF THE DRAWINGS
[0038] Now describe the utility model in detail according to the schematic diagram:
[0039] exist Figure 1 The reduction gear unit with an especially optional additional cooling device is shown in an oblique view.
[0040] exist Figure 2 The reduction gear is shown open on the input side.
[0041] exist Figure 3 1 shows an exploded oblique view of a particularly optional additional cooling tube arrangement arranged on the input side in the reducer.
[0042] exist Figure 4 The cooling device of the reducer according to the present invention is shown in an exploded oblique view.
[0043] exist Figure 5 The cooling device of the reducer according to the present invention is shown in an oblique view.
[0044] List of reference numerals:
[0045] 1 shell
[0046] 2 input interfaces
[0047] 3 discharge interface
[0048] 4 bearing flange
[0049] 5 Input connector
[0050] 6 discharge connector
[0051] 7 Flange area
[0052] 20 Interface components
[0053] 21 Connectors
[0054] 22 ring groove
[0055] 30 Ring pipe
[0056] 31 Spacer
[0057] 40 raised part
[0058] 41 Cover DETAILED DESCRIPTION
[0059] As shown in the figure, the reducer has a housing part 1 which provides a flange region 7 on the input side of the reducer and which accommodates the bearing of the input shaft of the reducer.
[0060] On the side of the housing part 1 facing away from the flange region 7 , the housing part is connected to a bearing flange 4 which accommodates the bearing of an output shaft, in particular a hollow shaft.
[0061] Preferably, the reducer is designed as a coaxial reducer, in particular a planetary gear reducer.
[0062] like Figure 2 As shown, the collar region 7 has annular grooves 22 arranged concentrically with respect to one another.
[0063] The interface component 20 and the connecting member 21 are arranged in sequence along the radial direction. Here, the interface component 20 is arranged radially outside the connecting member 21.
[0064] Semi-annular annular tubes 30 are accommodated in the annular groove 22 and are each connected with their end regions, viewed in the circumferential direction, to a corresponding connecting piece 21 .
[0065] Here, each connecting piece 21 connects a first of the semicircular ring tubes 30 to a second semicircular ring tube 30 , which is arranged radially inside the first semicircular ring tube and within the same circumferential angle range as the first semicircular ring tube.
[0066] In the remaining circumferential angle range outside the aforementioned circumferential angle range, each connecting piece 21 further connects a third semicircular ring tube 30 to a fourth semicircular ring tube 30, which is arranged radially inside the third semicircular ring tube and within the same circumferential angle range as the third semicircular ring tube.
[0067] The supply connection 2 allows the coolant to be supplied to the connection part 20 via a channel formed in the housing part 1 .
[0068] The connection part 20 is connected to two radially outermost annular tubes 30 , which are connected diametrically opposite each other to the connection part 20 by means of first connecting pieces.
[0069] In this way, the cooling medium, in particular water or oil, flows through the radially outermost annular tube 30 within a first circumferential angle range and then gradually flows through the radially innermost annular tubes with corresponding alternating flow directions, that is, in particular in the circumferential direction or counter to the circumferential direction, until it reaches the radially innermost annular tube 30 designed as a complete ring, and the cooling medium thus flows back from the radial inside to the radial outside through the semicircular annular tubes within another circumferential angle range until it reaches the outermost semicircular annular tube 30, from where it is deflected through the interface part 20 and through the channel constructed in the housing part 1 to the discharge interface 3.
[0070] Overall, the cooling medium thus flows sequentially from radially outward to radially inward through the semi-annular annular canals 30 in the first half of the circumference until it reaches the substantially fully annular, radially innermost annular canal 30, and from there sequentially from radially inward to radially outward in the other half of the circumference. This implementation of heat dissipation in the flange area 7 allows for efficient heat dissipation on the input side. Importantly, the input shaft bearing and the adjacent shaft sealing ring serve as the two primary sources of heat loss.
[0071] The axial direction is parallel to the rotation axis of the input shaft, while the radial direction is based on the rotation axis of the input shaft. Similarly, the circumferential direction is also based on the rotation axis of the rotor shaft.
[0072] like Figure 4 and Figure 5 As shown, the cooling device according to the present invention is implemented on a housing part.
[0073] The coolant flows through an annular gap, on the radial inside of which radially oriented projections 40 are arranged, which generate turbulence in the coolant and thus dissipate heat more effectively from the housing part to the coolant.
[0074] The projections 40 are spaced apart from one another in the circumferential direction and are formed on a hollow-cylindrical bearing receptacle, from which each projection protrudes in a radially outward direction.
[0075] The cover plate 41 radially outwardly delimits an annular gap. The cover plate 41 has regions arranged one after the other in the circumferential direction, with folds formed between each region. Each of these regions is preferably flat or preferably has at least one flat region. The regions and their adjacent regions have a non-zero angle, that is, they are not parallel.
[0076] The cover plate 41 is placed on the projection 40 and thus defines and limits the spatial area for the cooling medium. The cover plate 41 is preferably connected to the projection 40 by welding.
[0077] Arranged on the housing part is an inlet connection 2 , which is connected via a channel formed in the housing part 1 to a spatial region for the cooling medium.
[0078] Arranged on the housing part is a drain connection 3 , which is connected via a channel formed in the housing part 1 to a spatial region for the coolant.
[0079] The heat dissipation of the retarder can therefore be achieved by means of two cooling devices—either provided simultaneously or alternatively.
[0080] In the region not covered by the cover plate 41 in the circumferential direction, the annular gap is realized as an annular groove of the housing part, wherein the radial outer side of the hollow-cylindrical bearing receptacle serves as the radial inner side of the annular gap.
[0081] In other embodiments according to the present invention, a plastic injection molded part is used instead of the cover plate 41 and bonded to the protrusion 40 instead of being welded.
Claims
1. A speed reducer comprising a housing and an input shaft. It is characterized by: An annular gap through which a coolant flows is formed between the cover plate and the housing of the reducer. The annular gap circumferentially surrounds a hollow cylindrical bearing receptacle formed on the housing. The bearing of the input shaft is received in the bearing receiving portion. The bearing receptacle is a hollow-cylindrical region of the housing part.
2. The reducer according to claim 1, It is characterized by: Protrusions are formed on the housing part, which are spaced apart from each other in the circumferential direction and protrude radially outward from the bearing receptacle toward the cover plate. and / or, The cover is placed flat on the raised part. and / or, The cover is connected to the projection in a materially bonded manner.
3. The reducer according to claim 2, It is characterized by: The longest dimension of the respective projection is in a direction transverse to the flow direction and / or in the axial direction, The flow direction of the cooling medium is oriented substantially in the circumferential direction.
4. The reducer according to claim 2 or 3, It is characterized by: The axial width of the corresponding projection is smaller than the axial width of the annular gap.
5. The reducer according to any one of claims 1 to 3, It is characterized by: The annular gap is delimited and / or covered radially outwardly by the cover plate.
6. The reducer according to any one of claims 1 to 3, It is characterized by: The cover plate consists of flat areas, between which folds are arranged.
7. The reducer according to any one of claims 1 to 3, It is characterized by: The annular gap is arranged within a circumferential angular range not covered by the cover plate in an annular groove section which is formed in the housing part and surrounds the bearing receptacle in the circumferential direction within this circumferential angular range.
8. The reducer according to any one of claims 1 to 3, It is characterized by: A flange region is formed on the housing part on the input side, in which annular grooves are formed which are arranged concentrically with respect to one another and with respect to the axis of rotation of the input shaft. A semicircular ring tube is received in the ring groove. Connecting parts and interface components are arranged on the flange area of the housing part. The connecting piece and the interface part are each pressed against the flange area by means of screws which are screwed into threaded holes in the flange area. The threaded member passes through the connecting member and the interface component.
9. The reducer according to claim 8, It is characterized by: Each of the connecting elements connects the semicircular annular tube in a first half-circumference to an adjacent annular tube arranged radially inwardly relative to the annular tube. and / or, Each of the connecting elements connects the semicircular annular tube in the other half of the circumference to an adjacent annular tube arranged radially inwardly relative to the annular tube. and / or, The connecting part connects the first channel formed in the housing part to the first opening of the radially outermost first semi-annular annular tube.
10. The reducer according to claim 9, It is characterized by: The connecting part connects the second channel formed in the housing part to the first opening of the radially outermost second semi-annular annular tube.
11. The reducer according to claim 8, It is characterized by: The radially innermost annular tube is designed as a complete annular tube and is connected to the radially innermost connecting piece.
12. The reducer according to claim 8, It is characterized by: Spacers are arranged radially between the ring tubes. The spacer is pressed against the flange area by means of the screw which is screwed into the threaded hole in the flange area.
13. The reducer according to claim 10, It is characterized by: The first channel opens into the inlet connection (5) and the second channel opens into the outlet connection (6).
14. The reducer according to claim 13, It is characterized by: The first channel extends in the axial direction and passes through the housing member, and / or, The second channel extends in the axial direction and passes through the housing member, and / or, The flange area has a through-bearing hole through which the input shaft passes. The bearing of the input shaft is received in the bearing bore.
15. The reducer according to claim 8 or 9, It is characterized by: Each ring tube is designed as a thin-sheet ring tube. The lamellae are continuous in the circumferential direction and project radially on the annular tube, and / or the lamellae are spaced evenly apart from one another on the annular tube.