CN106931146B

CN106931146B - Speed reducer with gear and housing consisting of lower part and upper part

Info

Publication number: CN106931146B
Application number: CN201511024628.6A
Authority: CN
Inventors: 邬自力
Original assignee: Sew Transmission Equipment Co ltd
Current assignee: SEW Eurodrive GmbH and Co KG
Priority date: 2015-12-30
Filing date: 2015-12-30
Publication date: 2021-06-18
Anticipated expiration: 2035-12-30
Also published as: CN106931146A

Abstract

The invention relates to a reduction gear having a gear wheel and a housing which is composed of a lower part and an upper part and is filled with oil, wherein an oil supply part is fastened to the lower part, in particular screwed to the lower part, wherein a channel is arranged between the gear wheel and the oil supply part, into which channel a line opens, wherein the channel is delimited by the oil supply part and the gear wheel, wherein the oil supply part forms and/or has a line.

Description

Speed reducer with gear and housing consisting of lower part and upper part

Technical Field

The invention relates to a reduction gear having a housing which comprises a lower part and an upper part and is partially filled with oil, and having a gear.

Background

It is generally known that a speed reducer has a housing and a gear.

Disclosure of Invention

The object of the invention is therefore to design a reduction gear with reduced power losses.

Said object is achieved according to the invention by a retarder according to the features of claim 1.

An important feature of such a gear unit according to the invention is that it is provided with a housing which is partially filled with oil and comprises a lower part and an upper part and has a gear wheel, wherein an oil feed/oil guide is fastened, in particular screwed, to the lower part, wherein a channel is arranged between the gear wheel and the oil feed, into which channel a conduit opens, wherein the oil feed and the gear wheel form the boundary of the channel, wherein the oil feed forms and/or has the conduit.

The advantage here is that oil can be transported from the lower part to the upper part, i.e. potential energy can be provided for the oil, so that the oil can be transported to a lubricating location which is not arranged in the oil sump and/or below the oil level.

In an advantageous embodiment, the line is arranged in a vertical orientation and/or the line leads from the oil sump of the gear unit to the channel. This has the advantage that the oil can be sucked out of the oil sump. The oil can thus be sucked out of the oil sump by the underpressure in the channel. This relative underpressure can be generated by a non-vanishing flow velocity in the channel. The teeth of the gear wheel rotating in this way carry the oil and in this way form a flow in the channel.

In an advantageous embodiment, the oil level is located inside the lower part, in particular, the oil sump is arranged in the lower part. The advantage here is that only air is present in the upper part and therefore as little mass as possible is present in the gear unit. The oil delivered by the rotating gear is delivered through a channel to a location to be lubricated, such as a bearing and/or a land, in the region of the cavity above the oil level. For this purpose, the collecting device, i.e. the means for collecting the oil that is centrifuged off vertically upwards, is important. The collected oil is then transported to the location to be lubricated.

In an advantageous embodiment, the oil conveyed through the channel is discharged vertically out of the channel, in particular such that the upper part is acted upon by the oil. The advantage here is that the oil even drips off from the inside of the upper part and can be collected, for example by means of a collecting trough or a basin-shaped collecting device.

In an advantageous embodiment, the means for collecting the oil discharged from the channel direct the collected oil to the lubrication point, in particular to the bearing and/or to the at least one engagement region. The advantage here is that the collected oil can be led to the lubrication point.

In an advantageous embodiment, the oil delivery part has a central plate part and two side plates, the central plate part being arranged between the side plates, wherein the passage is delimited by the gearwheel, the central plate part and the two side plates, in particular wherein the central plate part is screwed and/or welded to the respective side plate. The advantage here is that the channel can be formed in a simple manner.

In an advantageous embodiment, each side plate has a web region, in particular a web region bent at right angles, wherein the web region is fastened, in particular screwed, to the lower part. The advantage here is that a simple connection is achieved by placing on the finished surface of the lower part.

In an advantageous embodiment, the central panel has a section which functions as a barrel section/cylinder jacket section. The advantage here is that it can be produced simply.

In an advantageous embodiment, the central plate has an opening which acts as a junction for the pipe in the channel. The advantage here is that the inlet opening can be arranged in the center plate and thus the line opens directly into the channel.

In an advantageous embodiment, the central plate part has two spaced-apart, in particular parallel, tube wall sections for delimiting the duct, wherein each of the side plates has a respective side tube wall section for delimiting the duct, in particular wherein the side plates are spaced-apart from each other, in particular wherein each tube wall section is connected, in particular welded and/or screwed, to each side tube wall section for forming the duct. The advantage here is that the duct can be formed in a simple manner.

In an advantageous embodiment, the pipe has a rectangular cross section. The advantage here is that the punch-bending element can be used as a boundary and can therefore be produced in a simple manner.

In an advantageous embodiment, the axial region covered by the central plate is larger than the axial region covered by the gearwheel, in particular by the tooth of the gearwheel, in particular wherein the axial direction is arranged parallel to the rotational axis of the gearwheel, in particular parallel to an output shaft connected to the gearwheel in a rotationally fixed manner. The advantage here is that the oil transfer element does not contact the gear wheel and therefore there is no direct frictional loss. In addition, the intermediate region between the gear and the oil transfer element is filled with oil and is therefore lubricated very well.

In an advantageous embodiment, the radial distance region covered by the respective side plate comprises the radial distance region covered by the tooth of the gearwheel, wherein the central plate part is spaced apart from the gearwheel, in particular wherein the entire oil delivery part is spaced apart from the gearwheel, in particular wherein the radial distance is defined as the distance to the rotational axis of the gearwheel. The advantage here is that the gear wheel is surrounded by the oil feed in the region of the channel and that the oil can be fed in a targeted manner.

In an advantageous embodiment, the lower part has a finished surface with a bore for the threaded connection with the oil delivery part and on which the upper part is placed, in particular wherein the surface is designed flat, in particular wherein a seal is arranged between the lower part and the upper part. The advantage here is that this surface is designed to be slightly larger than the surface necessary for connecting the upper part with the lower part.

In an advantageous embodiment, the oil delivery element is formed as a punch-bending element. The advantage here is that the production of the oil transfer element can be carried out simply and cost-effectively.

Further advantages are specified in the dependent claims. The invention is not limited to the combination of features of the claims. Other possible combinations of the features of the claims and/or of the individual claims and/or of the features of the description and/or of the drawings may be made by those skilled in the art, especially if these are set forth in their task and/or by comparison with the prior art.

Drawings

The invention is described in detail below with reference to the accompanying drawings:

fig. 1 shows a gear unit according to the invention in an oblique view, the housing of which has a lower part 1 and an upper part 2 placed thereon.

Fig. 2 shows the reduction gear without the upper part 2, wherein the oil transfer element 20 is shown on a gear wheel 21 connected in a rotationally fixed manner to the drive shaft 3.

Fig. 3 shows an exploded view of fig. 2, in which the gear wheel 21 with the bearing of the output shaft 3 and the meshing part meshing with the gear wheel 21 and the bearing structure of the meshing part and the oil delivery part 20 can be seen, respectively.

Fig. 4 shows a cross-sectional view of the gear unit in an oblique view.

Fig. 5 shows the gear wheel 21 and the oil transfer element 20 in an oblique view.

Fig. 6 shows a cross-sectional view of the gear unit in plan view.

Fig. 7 shows the oil transfer element 20 in detail in an oblique view, wherein it is assembled from a central plate part 72 and two side plates 71.

An exploded view belonging to fig. 7 is shown in fig. 8.

Fig. 9 shows a first of the two side plates 71 in a perspective view.

Fig. 10 shows the other of the two side plates 71 in a perspective view.

Fig. 11 shows the center plate 72 in greater detail in an oblique view.

List of reference numerals:

1 lower part

2 Upper part

3 output shaft

20 oil transportation piece

21 gear wheel, in particular a gear wheel which is connected in a rotationally fixed manner to the output shaft 3

30 connecting surface

71 side plate

72 center plate

73 connecting plate section

74 tube wall section

75 side wall section

76 opening

110 cylinder segments, especially quarter cylinder shells

Detailed Description

As shown in the drawing, the gear unit has an upper part 2 which rests on a flange surface 30 of a lower part 1, which is designed to be flat. The upper part 2 and the lower part 1 are preferably made of steel castings.

The flange surface 30 is designed to be flat and finished, so that a seal, in particular a flat seal, can be arranged on the flange surface 30 between the upper part 2 and the lower part 1 and thus connect the lower part 1 and the upper part 2 in an oil-tight manner.

Holes, in particular threaded holes, are provided in the flange surface 30, so that the upper part 2 and the lower part 1 can be screwed together.

The oil delivery element 20 is screwed into a threaded bore, which is not covered by the upper element 2 and is arranged in the flange surface 30, a threaded element is screwed into this threaded bore, and the head of the threaded element presses the web section 73 of the oil delivery element 20 against the lower part 1.

The bearing receptacle of the bearing supporting the output shaft 3 is designed in two parts. For this purpose, the lower part 1 has a semicircular recess which is finished and into which the bearing of the output shaft 3 is inserted. The upper part has a corresponding semicircular recess which is likewise finished and receives the surface section of the bearing which is not received by the lower part 1.

The output shaft is connected in a rotationally fixed manner to the gear wheel 21, in particular by means of a key connection.

The oil delivery member 20 is threadedly coupled to the lower member 1 and forms an oil delivery passage between the gear 21 and the oil delivery member 20. The oil delivery element 20 is spaced apart from the toothing of the gear wheel 21 and follows approximately 90 °, i.e. a quarter of the circumference of the gear wheel 21. The oil channel is thus designed from the oil sump of the reduction gear up to a peripheral position on the rolling circle of the gear wheel with a vertical tangent. The transported oil is thus centrifuged out of the oil channel substantially vertically. In this way, the location to be lubricated in the upper part is also acted on by the oil. In particular, however, it is also possible to collect the oil that is thrown off centrifugally upwards and to guide the collected oil to the location to be lubricated, such as the bearing and/or the joint region of the two toothed segments.

For this purpose, the oil transfer part 20 has a vertically oriented pipe for drawing oil from an oil sump. This pipe conveys oil into an oil delivery channel formed between the gear and the oil delivery member 20. Because the oil moves rapidly in the oil transfer channel, there is less pressure than in the oil sump. In this way, oil is sucked out of the oil sump through the pipe into the oil transfer channel and is thrown off centrifugally, substantially vertically, at the outlet of the oil transfer channel.

The oil delivery element 20 is formed by a central plate element 72 and two side plates 71, the central plate element 72 being arranged between the two side plates 71. The width of the center plate 72 is slightly greater than the width of the gear 21.

The two parallel tube wall sections 74 of the central plate 72 and the tube wall sections 75 of the two sides of the side plates 71 form the boundaries of the duct.

The central plate 72 thus has a quarter-circular section 110, which corresponds to a quarter of the cylinder. This section 110 can therefore also be referred to as a quarter-cylinder 110. An opening 76 is formed in the lower region of the portion 110, which opening acts as a junction for the pipe into the oil supply line. From this opening in the central plate 72, two parallel tube wall sections 74 extend vertically downwards. In the axial direction, the spacing region between the two tube wall sections 74 for forming a tube is closed by the lateral tube wall sections 75 of the first side plate 71. In the axially opposite direction, the spacing region between the two pipe wall sections 74 for forming the pipe is closed by a side pipe wall section 75 of the further side plate 71 which is designed mirror-symmetrically to the first side plate 71.

Each side plate 71 has on its upper side a web section 73 for connection to the lower part 1.

The side tube wall sections 75 are formed on the lower side of the corresponding side plates 71.

The side plates 71 and the center plate member 72 are preferably made of steel plates as punching and bending members, respectively.

The side plates 71 each cover a radial distance region, in particular based on the axis of rotation of the gearwheel 21, which covers the radial distance region covered by the toothing and the oil supply channel.

The side plates 71 are each screwed and/or welded to the central plate member 72.

Claims

1. A gear unit with a gear wheel and a housing which is composed of a lower part and an upper part and is partially filled with oil, an oil sump being arranged in the lower part, characterized in that an oil delivery member is fastened to the lower part, a channel being arranged between the gear wheel and the oil delivery member, which channel is delimited by the oil delivery member and the gear wheel, and in that the oil delivery member has a conduit which opens into the channel,

the oil delivery member has a central plate member and two side plates, the central plate member being arranged between the two side plates, wherein the passage is delimited by the gear, the central plate member and the two side plates,

the oil transfer member is spaced from the tooth of the gear and follows a quarter of the circumference of the gear, so that the channel is designed to extend from the oil sump of the reduction gear to a circumferential position on the rolling circle of the gear with a vertical tangent, so that the oil transferred through the channel is discharged vertically from the channel, so that the upper part is acted upon by the oil.

2. A decelerator according to claim 1, wherein the oil delivery member is threadedly attached to the lower member.

3. A reducer according to claim 1 or claim 2, in which the conduit is oriented vertically and/or the conduit leads from an oil sump of the reducer to the passage.

4. A reducer according to claim 1 or claim 2, in which the oil level is internal to the lower member.

5. A reducer according to claim 1 or claim 2, in which the means for collecting oil discharged from the passage directs the collected oil to the lubrication point.

6. A reducer according to claim 5, in which the lubrication location is a bearing and/or at least one toothed engagement region.

7. A reducer according to claim 1 or claim 2, in which the centre plate member is screwed and/or welded to the respective side plate.

8. A reducer according to claim 1 or claim 2, in which each side plate has a web region, wherein the web regions are secured to the lower member.

9. A reducer according to claim 8, in which the web regions are bent at right angles.

10. A reducer according to claim 8, in which the web region is screwed onto the lower member.

11. A decelerator according to claim 1 or claim 2 wherein the centre plate has a section which functions as a barrel section.

12. A decelerator according to claim 1 or claim 2 wherein the central plate member has an opening which serves as a sink for a conduit into the passage.

13. A reducer according to claim 1 or 2, in which the centre plate has two spaced-apart tube wall sections for defining the duct, wherein each of the side plates has a side tube wall section for defining the duct, wherein the side plates are spaced-apart from each other, wherein each tube wall section is connected to each side tube wall section for forming the duct.

14. A decelerator according to claim 13 wherein the tube wall sections are parallel to each other.

15. A decelerator according to claim 13 wherein each tube wall section is welded and/or threaded to each side tube wall section.

16. Decelerator according to claim 1 or 2, wherein the duct has a rectangular cross-section.

17. A reducer according to claim 1 or 2, in which the axial area covered by the centre plate is greater than the axial area covered by the gear wheel, wherein the axial direction is arranged parallel to the axis of rotation of the gear wheel.

18. A reducer according to claim 17, in which the axial area covered by the centre plate is greater than the axial area covered by the teeth of the gears.

19. A reducer according to claim 17, in which the axial direction is arranged parallel to an output shaft to which the gear is connected in a non-rotatable manner.

20. A reducer according to claim 1 or 2, in which the radial distance zones covered by the respective side plates comprise the radial distance zones covered by the teeth of the gears, in which the radial distance is defined as the distance to the axis of rotation of the gears.

21. A decelerator according to claim 20, wherein the entire oil delivery member is spaced from the gear.

22. A reducer according to claim 1 or claim 2, in which the lower member has a finished surface with a bore for threaded connection with the oil transfer member, the upper member resting on the surface.

23. A reducer according to claim 22, in which the surface is designed to be flat.

24. A decelerator according to claim 22 wherein a seal is provided between the lower and upper members.

25. A reducer according to claim 1 or 2, in which the oil transfer member is formed as a punched and bent member.