reducer

Abstract

The utility model relates to a kind of reducers, it has the shaft supported in rotatable manner by bearing, especially still have non-contact sealing device, the inner ring of bearing is sleeved on the shaft, the outer ring of bearing is received in the shell part of reducer, especially bearing flange, first labyrinth disc and second labyrinth disc are fixed on bearing flange, ring part is sleeved on the shaft, the outer diameter of ring part monotonically decreases with the increase of axial distance from bearing, radial outer tip of ring part extends into the notch of second labyrinth disc, and it is directed to the cylindrical bottom surface of notch especially in order to produce pressure gradient.

Description

Technical Field

[0001] This utility model relates to a speed reducer. Background Technology

[0002] It is generally known that the reducer must be sealed to prevent oil leakage. Utility Model Content

[0003] Therefore, the purpose of this invention is to improve the speed reducer in a way that is both oil-tight and energy-efficient.

[0004] According to this invention, this objective is achieved by a speed reducer with the following features.

[0005] The reducer according to this utility model has a shaft rotatably supported by bearings and, in particular, a non-contact sealing device. A key feature of this reducer is that the inner ring of the bearing is fitted onto the shaft, and the outer ring of the bearing is received within the reducer's housing components, particularly the bearing flange.

[0006] The first and second maze disks are fixed to the bearing flange.

[0007] The shaft is fitted with a ring component, the outer diameter of which monotonically decreases as the axial distance from the bearing increases.

[0008] The radially outer tip of the ring component extends into the notch of the second labyrinth disk and extends toward the cylindrical bottom surface of the notch, especially to generate a pressure gradient.

[0009] One advantage here is that a non-contact sealing device can be installed on the reducer. Therefore, oil leakage is reliably prevented even though the reducer is at least partially filled with oil. Furthermore, the reducer is constructed with high energy efficiency through the non-contact sealing device. According to this invention, the ring component generates a pressure steepness due to its radially inwardly pointing, axially unilaterally inclined tip or ring edge, which reacts with the outflow of oil. However, the labyrinth seal also functions additionally, thus making the non-contact sealing device generally very safe and reliable in preventing oil leakage.

[0010] In an advantageous design, the outer diameter of the ring component—especially starting from its maximum value—decreases proportionally, especially monotonically, and especially strictly monotonically, to its axial distance from the bearing. The advantage here is that the tip or ring edge is unilaterally inclined, thus generating a pressure gradient that reacts to the oil outflow.

[0011] In an advantageous design, the cylindrical base has a constant radial distance to the axis of rotation of the shaft. The advantage here is that the base is implemented as a cylinder.

[0012] In an advantageous design, a slotted / grooved disc, particularly a shaft nut, is arranged on the shaft, wherein the slotted disc has a radially outward-opening slot. The advantage here is that the slotted disc can be implemented as a shaft nut and maintain the bearing preload. Therefore, the bearing can be implemented as an angular contact bearing / skewer bearing. Furthermore, the radial slot prevents the axial passage or outflow of oil.

[0013] In an advantageous design, the slotted disc has radially inwardly opening radial slots, specifically, these radially inwardly opening radial slots are axially spaced from radially outwardly opening radial slots. The advantage here is that oil is difficult to pass through or is even prevented from passing through.

[0014] In an advantageous design, an annular disc is incorporated into the bearing flange.

[0015] The axial region covered by the annular disk includes the axial region covered by the slotted disk or overlaps with the axial region covered by the slotted disk.

[0016] An annular gap, serving as a free space, is constructed between the slotted disc and the annular disc.

[0017] In particular, in the region covered axially by the annular gap, the slotted disc has radially outwardly opening radial slots on its radially outer periphery.

[0018] In particular, the annular disc is received in and / or adjacent to the outer ring bearing housing. An advantage here is that the annular disc can create a barrier for oil passing through the bearing, as the size of the annular clearance can be designed to be very narrow, especially within tolerances.

[0019] In an advantageous design, the slotted disc is axially positioned between the inner ring and the ring assembly. The advantage here is that the slotted disc transmits the bearing preload directly to the inner ring, or via an intermediately positioned ring.

[0020] In an advantageous design, a first bushing is fitted onto the shaft, on which radially outward protrusions, particularly centrifugal oil-throwing edges, are constructed. These protrusions extend axially into the gap between the first and second labyrinth disks. The advantage here is that oil can be thrown out and thus prevented from passing through.

[0021] In an advantageous design, the second labyrinth disk has an annular groove on its radially inner side.

[0022] In the region covered by the annular groove in the axial direction, the first bushing has a cylindrical first radial outer periphery.

[0023] In particular, the annular groove is designed to be open toward the cylindrical outer surface of the first radial outer periphery. This has the advantage of preventing oil from flowing axially, especially by means of a pressure gradient generated by the cylindrical radial outer periphery of the bushing in the axial region covered by the annular groove.

[0024] In a favorable design, the first labyrinth disk also has another annular groove on its radially inner side.

[0025] In the region covered by the other annular groove in the axial direction, the first bushing also has a cylindrical second radial outer periphery.

[0026] In particular, the other annular groove is designed to be open to the cylindrical outer surface of the second radially outer periphery. This has the advantage of preventing oil from flowing axially, especially by means of a pressure gradient generated by the cylindrical radially outer periphery of the bushing in the axial region covered by the annular groove.

[0027] In an advantageous design, a second bushing is fitted onto the shaft, axially abutting and particularly abutting the first bushing. This allows for the gradual assembly of the sealing device.

[0028] In an advantageous design, a flanged disc is fitted onto the second bushing, the flanged disc—particularly by means of at least one radially threaded element—connecting to the second bushing in a manner that prevents relative rotation. The advantage here is that not only can barriers to prevent oil passage and centrifugal oil-throwing edges be provided on the radially inner side, but also a labyrinth can be provided on the axial end region, i.e., on the end side of the first labyrinth disc.

[0029] In an advantageous design, the flange disk has a plurality of axially oriented protrusions that extend into a plurality of concentrically arranged and spaced-apart annular grooves constructed on the axial end side of the first labyrinth disk.

[0030] In particular, the plurality of annular grooves are open in the axial direction. An advantage here is that the entire sealing device is arranged sequentially in the axial direction as a series of individual sealing components and can be assembled accordingly.

[0031] In an advantageous design, a spacer is provided between the first labyrinth disk and the second labyrinth disk. The advantage here is that the spacer defines a free space in which oil ejected from the centrifugal slinger edge can be received and guided back to the oil sump of the reducer at the lower end.

[0032] In an advantageous design, at least one axially oriented screw, screwed into a threaded hole in the bearing flange, presses a first labyrinth disc against the bearing flange with its head. This causes the first labyrinth disc to press a spacer onto a second labyrinth disc, and thus presses the second labyrinth disc firmly onto the bearing flange. The advantage here is that both labyrinth discs are fixed to the bearing flange. Preferably, a plurality of such screws are provided, wherein the screws are arranged at the same radial distance and are evenly spaced apart from each other in the circumferential direction.

[0033] This invention is not limited to the above-described combination of features. Those skilled in the art, particularly those seeking to achieve their intended purpose and / or through comparison with the prior art, can discern other reasonable combinations of the above-described features and / or individual features described above and / or features described below and / or features in the accompanying drawings. Attached Figure Description

[0034] The present invention will now be explained in detail with the aid of schematic diagrams:

[0035] Figure 1 The speed reducer according to the present invention is shown in longitudinal sectional view.

[0036] Figure 2 A magnified view of a part is shown.

[0037] List of reference numerals in the attached diagram:

[0038] 1 Ring component

[0039] 2. Circular disk

[0040] 3. Bearings, especially rolling bearings

[0041] 4. Slotted discs, especially shaft nuts

[0042] 5 First bushing

[0043] 6 Second bushing

[0044] 7. Flange disc

[0045] 8 screws

[0046] 9. First Maze Disc

[0047] 10 Second Maze Disc

[0048] 11. Housing components, especially bearing flanges

[0049] 12-axis

[0050] 20 Centrifugal oil slingshot edge

[0051] 21 First annular groove

[0052] 22 Second annular groove Detailed Implementation

[0053] As shown in the figure, the inner ring of bearing 3, especially rolling bearing, especially angular contact bearing, is fitted onto shaft 12, and the outer ring of bearing 3 is received in bearing flange 11.

[0054] An annular disk 2 is also received in the bearing flange 11. The annular disk preferably has the same outer diameter as the outer ring of the bearing 3. Therefore, the annular disk 2 can be received in the axially extended bearing housing of the bearing 3, which is constructed in the bearing flange 11 to receive the bearing 3.

[0055] A slotted disc 4 containing radial slits, and especially a shaft nut, are arranged on the shaft 12. As a result, oil passing through the bearing 3 splashes radially during the rotational movement of the shaft 12 and the slotted disc 4, which is connected to the shaft in a manner that prevents relative rotation.

[0056] The slotted disc 4 also has a radially oriented slot on its radially inner side, which prevents the oil flowing between the shaft 12 and the slotted disc 4 from continuing to flow, especially by capturing the oil by means of centrifugal force.

[0057] On the axial side of the slotted disc 4 facing away from the bearing 3, a ring component 1 is fitted onto the shaft 12. The radial outer diameter of the ring component decreases with increasing axial distance from the slotted disc 4 or the bearing 3, and in particular decreases proportionally to this distance. Thus, the ring component 1 has a sharp tip that points radially outward and generates a pressure differential that carries the oil back.

[0058] For this purpose, the ring component 1 extends into the notch of the second labyrinth disk 10 and points towards the bottom region of the notch, while maintaining a constant radial distance from the bottom region.

[0059] The notch is manufactured in the form of an annular groove, wherein the notch is designed to open towards the slotted disc 4 in the axial direction.

[0060] A first maze disk 9 is arranged axially spaced next to the second maze disk 10, wherein the two maze disks 9 and 10 are fixed to the bearing flange 11 by means of axially pointing screws.

[0061] A first annular groove 21 is machined in the radially inner side of the first labyrinth disk 9. A bushing 5 is pushed onto the shaft 12. This bushing has a first cylindrical surface, wherein the area covered by the first cylindrical surface in the axial direction includes the area covered by the annular groove in the axial direction. This prevents or at least reduces the flow of oil.

[0062] A second annular groove 22 is machined in the radially inner side of the second labyrinth disk 10. The bushing 5 has a second cylindrical surface, wherein the area covered by the second cylindrical surface in the axial direction includes the area covered by the second annular groove 22 in the axial direction. In this way, oil flow is prevented or at least reduced.

[0063] The bushing 5 has a radially inwardly protruding centrifugal oil-throwing edge 20 between the first cylindrical surface and the second cylindrical surface along the axial direction. Oil thrown out from this centrifugal oil-throwing edge enters the free space arranged axially between the first labyrinth disk 9 and the second labyrinth disk 10. The oil returns to the oil sump of the reducer at the lower position.

[0064] A second bushing 6 is fitted onto the shaft 12, and a flange disc 7 is then fitted onto the second bushing and—particularly by means of at least one radially oriented screw 8—in a non-rotatable manner. This flange disc has a plurality of axially projecting annular protrusions, particularly annular flanges. These protrusions are radially spaced apart from each other, concentrically implemented, and each extends into a corresponding annular groove machined in the first labyrinth disc 9. In this way, a high degree of safety against oil leakage is achieved.

[0065] The first bushing 5 is arranged axially next to the second bushing 6, and in particular, the two bushings 5 ​​and 6 are in contact with each other. Alternatively, the two bushings can be implemented together as a single bushing, thus requiring high precision during installation and manufacturing. In the two-piece embodiment, the positioning of the protrusion can be implemented independently of the annular grooves 21 and 22.

[0066] The annular gap between the annular disc 2 and the slotted disc 4 is very narrow, so that the ring component 1 also achieves oil separation through the pressure gradient generated by its tip rotating on the shaft 12.

[0067] The ring component 1 is axially arranged between the second bushing 5 and the slotted disc 4.

[0068] The slotted disc 4 is axially arranged between the ring component 1 and the inner ring of the bearing 3.

[0069] The flange 7 is fitted onto the second bushing 6 and thus radially surrounds the second bushing. The area covered by the flange 7 in the axial direction includes the area covered by the second bushing 6 in the axial direction.

[0070] The second maze disc 9 covers not only the area of ​​the first bushing 5 but also the area of ​​the second bushing 6 along the axial direction.

[0071] The axial direction is parallel to the rotation axis of shaft 12. The circumferential direction, radial direction, and radial distance are always based on the rotation axis of shaft 12.

[0072] At least one screw is screwed into the threaded hole of the bearing flange and its head presses the first labyrinth disk 9 against the second labyrinth disk 10 through a spacer, thereby pressing the second labyrinth disk against the bearing flange 11.

Claims

1. A speed reducer having a shaft rotatably supported by bearings and a non-contact sealing device. The inner ring of the bearing is fitted onto the shaft, and the outer ring of the bearing is received in the housing component of the reducer, which is the bearing flange. Its features are, A first labyrinth disk and a second labyrinth disk are fixed on the bearing flange. A ring component is fitted onto the shaft, and the outer diameter of the ring component monotonically decreases as the axial distance from the bearing increases. The radially outer tip of the ring component extends into the notch of the second labyrinth disk and extends toward the cylindrical bottom surface of the notch.

2. The reducer according to claim 1, Its features are, The outer diameter of the ring component decreases proportionally to its axial distance from the bearing.

3. The reducer according to claim 1 or 2, Its features are, The cylindrical base has a constant radial distance from the axis of rotation of the shaft.

4. The reducer according to claim 1 or 2, Its features are, A slotted disc is arranged on the shaft, and the slotted disc is implemented as a shaft nut. The slotted disc has radially outward-opening radial slots.

5. The reducer according to claim 4, Its features are, The slotted plate has radially inward-opening radial slots. The radially inwardly opening radial slot is axially spaced from the radially outwardly opening radial slot.

6. The reducer according to claim 4, Its features are, An annular disc is received in the bearing flange. The axial region covered by the annular disk includes the axial region covered by the slotted disk or overlaps with the axial region covered by the slotted disk. An annular gap is constructed between the slotted disc and the annular disc to serve as free space. In the region covered by the annular gap in the axial direction, the slotted disc has a radially outwardly opening radial slot on its radially outer periphery. The annular disk is received in the bearing housing of the outer ring and / or adjacent to the outer ring.

7. The reducer according to claim 4, Its features are, The slotted disc is arranged axially between the inner ring and the ring component.

8. The reducer according to claim 1 or 2, Its features are, A first bushing is fitted onto the shaft, and a radially outwardly protruding portion is constructed on the first bushing, which is implemented as a centrifugal oil-slinging edge. The protrusion extends into the free space between the first and second labyrinth disks, which are constructed axially.

9. The reducer according to claim 8, Its features are, The second maze disk has an annular groove on its radially inner side. In the region covered by the annular groove in the axial direction, the first bushing has a cylindrical first radial outer periphery. This allows the annular groove to be designed to open towards the cylindrical outer surface of the first radial outer periphery.

10. The reducer according to claim 9, Its features are, The first maze disk has another annular groove on its radially inner side. In the region covered by the other annular groove in the axial direction, the first bushing has a cylindrical second radial outer periphery. This allows the other annular groove to be made open to the cylindrical outer surface of the second radial outer periphery.

11. The reducer according to claim 8, Its features are, A second bushing is fitted on the shaft, and the second bushing is axially adjacent to the first bushing, with the second bushing abutting against the first bushing.

12. The reducer according to claim 11, Its features are, A flange is fitted onto the second bushing, and the flange is connected to the second bushing in a manner that prevents relative rotation, the connection being achieved by means of at least one radially oriented screw.

13. The reducer according to claim 12, Its features are, The flange disk has a plurality of axially oriented protrusions that extend into a plurality of concentrically arranged and spaced-apart annular grooves constructed on the axial end side of the first labyrinth disk. The plurality of annular grooves open along the axial direction.

14. The reducer according to claim 1 or 2, Its features are, Spacers are placed between the first and second maze boards.

15. The reducer according to claim 14, Its features are, At least one axially oriented screw, screwed into a threaded hole in the bearing flange, presses the first labyrinth disc against the bearing flange with its screw head, thereby pressing the spacer onto the second labyrinth disc and thus pressing the second labyrinth disc tightly onto the bearing flange.

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