GEARBOX WITH A HOUSING PART, A FIRST COVER PART AND A SECOND COVER PART

Description

[0001] The invention relates to a transmission with a housing part, a first cover part and a second cover part.

[0002] It is generally known that a gearbox has a housing part in which bearings are housed.

[0003] From KR 101 933 118 B1, the closest prior art is known a transmission with a housing part which shows the features of the preamble of claim 1.

[0004] A bevel gear is known from CN 204 729 551 U.

[0005] A worm gear is known from CN 202 195 000 U.

[0006] The invention is therefore based on the object of operating a transmission safely.

[0007] According to the invention, the object is achieved in the transmission according to the features specified in claim 1.

[0008] The advantage here is that the ring wall gives the gearbox a double wall, thus reducing the internal space. This also reduces the amount of lubricant in the interior. This also results in a smaller pressure change during temperature fluctuations, which reduces the stress on the seals and thus improves the sealing and thus the degree of protection. Grease is the preferred lubricant, or alternatively, gear oil.

[0009] By using identical cover parts, manufacturing costs can be reduced. Another advantage is that a filler material or air can be arranged in the radial intermediate region between the outer wall and the first and / or second wall region, which filler material is preferably separate from the interior of the gearbox, which is at least partially filled with lubricant. In this way, the associated pressure changes can be reduced when temperature changes occur during operation, and this in turn improves sealing, since the seals are exposed to the smaller pressure differences between the interior and the environment. Another advantage is that the driving shaft is provided with sufficient space, while the internal volume, which is at least partially filled with lubricant, can still be reduced.Another advantage is that the bearings can be accommodated in the cover parts, particularly in the first ring areas of the two identically constructed cover parts. Support can be provided by the housing part on the radial outer side of the first ring area. Another advantage is that the transition area stabilizes the double wall. By using a smooth ring wall, notch effects are reduced and high load capacity is therefore achievable. In particular, the sealing ring is stably accommodated when loads such as transverse forces or the like occur, and the seal is therefore not compromised. Another advantage is that the driving shaft is provided with sufficient space and therefore also lubricant, but the internal volume of the gearbox can be reduced as much as possible.

[0010] In an advantageous embodiment, the intermediate area between the outer wall and the first wall area is axially continuous through the housing part. This is advantageous in that even in the area axially covered by the toothed part, a reduction in the

[0011] internal volume can be achieved and a high level of rigidity can be achieved due to the axially elongated double wall.

[0012] In an advantageous embodiment, the intermediate area between the outer wall and the second wall area is axially continuous through the housing part. This is advantageous because the internal volume can be reduced even in the area axially covered by the gearing part, and high rigidity is achieved thanks to the axially elongated double wall.

[0013] In an advantageous embodiment, the intermediate region between the outer wall and the first wall region consists of air or a filler material. The advantage here is that when air is used, the intermediate region can be separated from the internal volume. When filler material is used, the intermediate region can advantageously be used as a reservoir for lubricant, which can be supplied to the lubrication points during operation. In particular, an electrically controllable heating element can be arranged in the intermediate space region so that when the gear has cooled down, the intermediate region can be heated up quickly and, due to the resulting increase in the pressure difference to the internal volume of the gear, i.e. to the spatial area of the gear comprising the gear teeth, lubricant can be conveyed to the lubrication points, preferably through recesses that lead from the intermediate region to the internal volume.

[0014] In an advantageous embodiment, the intermediate region between the outer wall and the second wall region consists of air or a filler material. The advantage here is that when air is used, the intermediate region can be separated from the internal volume. When filler material is used, the intermediate region can advantageously be used as a reservoir for lubricant, which can be fed to the lubrication points during operation. In particular, an electrically controllable heating element can be mounted in the intermediate space region so that when the gear has cooled down, the intermediate region can be heated up quickly and, due to the resulting increase in the pressure difference to the internal volume of the gear, i.e. to the spatial area of the gear containing the gear teeth, lubricant can be fed to the lubrication points, preferably through recesses that lead from the intermediate region to the internal volume.

[0015] In an advantageous embodiment, the filler material contains a lubricant that can be directed to lubrication points, particularly bearings or the meshing area of gears, of the transmission. This is advantageous in that friction can be reduced and the service life of the transmission increased, particularly by reducing friction-related heat loss.

[0016] According to the invention, the first wall region is connected to the outer wall via a connecting wall region at its axial end region facing the toothed part connected to the shaft in a rotationally fixed manner, wherein the connecting wall region extends radially, and / or wherein the region covered in the axial direction by the first wall region is spaced apart from the region covered in the axial direction by the toothed part. The advantage here is that sufficient space is available for the toothed part. Thus, a toothed part of such a size can be used that only the outer wall can be arranged between the toothed part and the surrounding area. Nevertheless, the amount of lubricant is reduced because the internal volume is reduced.

[0017] In an advantageous embodiment, the area covered in the axial direction by the first wall region overlaps the area covered in the axial direction by the driving shaft. This is advantageous because the first wall region does not occupy the space of the driving shaft. Thus, the internal volume can be reduced by means of the first wall region, while the driving shaft can operate without disruption.

[0018] In an advantageous embodiment, the driving shaft is spaced axially from the second wall region. It is advantageous that the second wall region is spaced in the area subjected to stress by the driving shaft.

[0019] In an advantageous embodiment, the first cover part is identical and / or structurally identical to the second cover part. This is advantageous in that a small number of parts are required. A bearing can always be accommodated in the first ring region. Alternatively, a support by the housing part and a first sealing ring can be arranged on the radial outer side of the first ring region, or alternatively, a second sealing ring can be provided on the second ring region of the cover part, which is spaced apart from the first, so that the bearing and the seal can be decoupled.

[0020] In an advantageous embodiment, the radial clearance area covered by the driving shaft encompasses the radial clearance area covered by the first wall area. This is advantageous because the wall area is located in the same radial area while still providing sufficient space for the driving shaft.

[0021] In an advantageous embodiment, the radial clearance area covered by the driving shaft encompasses the radial clearance area covered by the second wall area. This is advantageous because the wall area is located in the same radial area while still providing sufficient space for the driving shaft.

[0022] In an advantageous embodiment, the second bearing is accommodated by the first annular region of the second cover part, in particular on its radial inner side. Advantageously, the bearing is decoupled from the second sealing ring arranged on the second annular region of the second cover part.

[0023] In an advantageous embodiment, the toothed part is arranged closer to the second bearing than to the first bearing. This is advantageous because introduced transverse forces can be absorbed by the first ring area and the second sealing ring is separated from deflections of the first bearing.

[0024] In an advantageous embodiment, the toothed part engages with a toothing of an input shaft or with a toothing of a part connected to the input shaft, wherein the rotational axis of the input shaft is oriented perpendicular to the rotational axis of the toothed part, in particular wherein the rotational axis of the toothed part is spaced from the rotational axis of the input shaft. Advantageously, the invention is applicable to an angular gear stage of a transmission.

[0025] Further advantages arise from the subclaims.

[0026] The invention will now be explained in more detail using schematic illustrations: In the Figure 1 is a cross-section through a cover part 1 of a transmission according to the invention. Figure 2 a cross section through a housing part 20 of the transmission according to the invention is shown. Figure 3a plan view of a housing part 20 of the transmission according to the invention is shown. Figure 4 A cross-section through the transmission according to the invention is shown. Figure 5 A top view of the transmission according to the invention is shown. Figure 6 a housing part 20 of a similar transmission is shown in an oblique view, wherein here an S-shaped transition area 24 is designed instead of a step-shaped transition area in a double wall formed by wall areas 25, 26. In the Figure 7 This housing part 20 is shown from a different perspective. Figure 8 is a longitudinal section through the Figure 6 and Figure 7 The corresponding gearbox is shown. Figure 9 is one to Figure 8 corresponding side view is shown, which shows the cutting surface of the Figure 8 characterized. In the Figure 10 is one of the Figures 8 and 9 corresponding cross-section is shown. In the Figure 11is one to Figure 10 corresponding side view is shown, which shows the cutting surface of the Figure 10 characterized.

[0027] As in the Figures 1 to 5 As shown, the transmission has a housing part 20 which is arranged between two cover parts 1 which are identical to one another.

[0028] The first of the two cover parts 1 accommodates a first bearing 41 of an output shaft 40.

[0029] The second of the two cover parts 1 accommodates a second bearing 46 of the output shaft 40.

[0030] Thus, the output shaft 40 is rotatably mounted by means of the two bearings (41, 46) and projects through the first cover part 1.

[0031] In the axial direction, i.e. in the direction of the axis of rotation of the output shaft 40, a shaft sealing ring 42 is accommodated in the first cover part 1 next to the first bearing 41, which seals towards the output shaft 40.

[0032] A first annular region 5, in particular a ring-like projection, is formed on the first cover part 1, which projects into the interior of the gearbox and has a seat 2 for the first bearing 41 on its radial inner side and a seat 3 for a first sealing ring 43 on its radial outer side. Radially spaced from the first annular region 5 on the first cover part 1 is a further annular region 6, which also has a seat 4 for a further sealing ring on its radial outer side. This seat 4 is not claimed, i.e. not used, in the first cover part 1, but is used in the second cover part 1, which has the second bearing 46 on the radial inner side of its first annular region 5 and the seat 4, against which a second sealing ring 44 rests, on the radial outer side.

[0033] This second sealing ring 44 is arranged between a seat 22 formed on the housing part 20 and the seat 4 of the second cover part 1.

[0034] Both seats (4, 22) are not machined after the production of the two parts, in particular the housing part 20 and the cover part 1. Thus, the sealing ring 44 rests against a correspondingly rough surface.

[0035] The second ring area of the second cover part 1 is inserted into a cylindrical receptacle of the housing part 20 in the axial direction, whereby the second sealing ring 44 in the radial direction

[0036] direction between the seats 4 and 22 and therefore expands in the axial direction and counter to the axial direction.

[0037] A rounded area of the cover part 1 is connected to the seat 4. Similarly, another rounded area is connected symmetrically to the seat 22.

[0038] The tube-like space area formed between the seats 4 and 22, including the connected rounded areas, is therefore further extended axially than in the opposite direction to the axial direction.

[0039] The first ring region 5 of the first cover part 1 is inserted into a cylindrical receptacle which is arranged at a smaller radial distance than the receptacle provided for the second ring region of the second cover part.

[0040] A rounded region of the first ring region 5 is connected to the seat 3 of the first cover part 1, which is formed as a cylindrical surface section on the radially outer side of the first ring region. A rounded region is connected to the seat 21, which is formed as a cylindrical inner surface section, on the housing part 20, so that the first sealing ring is also arranged in a tubular space region delimited by the two cylindrical seats 3 and 21 and the two axially connected rounded regions.

[0041] The receptacle of the first ring region 5 in the housing part 20 is formed by a ring-like, axially directed projection of the housing part 20.

[0042] In this case, this projection has a first wall region 25 in a first circumferential angular range related to the axis of rotation of the output shaft 40 and a second wall region 26 in a second circumferential angular range spaced apart from the first circumferential angular range in the circumferential direction.

[0043] In a circumferential angle region arranged in the circumferential direction between the first and the second, a step-shaped transition region 24 from the first to the second wall region is formed.

[0044] This is because the first wall region 25 extends further in the axial direction from the axial end of the projection of the housing part 20 than the second wall region 26.

[0045] The embodiment according to the Figures 6 to 11differs in the shape of the transition region 24, which is not stepped but smooth, particularly S-shaped. The axial extension of the double wall formed by the wall regions 25 and 26 thus transitions smoothly from a first value to a second value, particularly in a continuously differentiable manner, particularly S-shaped.

[0046] The preferably S-shaped design reduces notch effects, enables easier production by casting and a more homogeneous material flow.

[0047] The radial width of the double wall, i.e. the double wall formed from the wall regions 25 and 26 and the transition region 24, is preferably constant.

[0048] The axial extension in the first wall region 25 is constant, in particular independent of the first circumferential angle range.

[0049] The axial extension in the second wall region 26 is constant, in particular independent of the second circumferential angle range.

[0050] As in Figure 8 and 10 As can be seen, the double wall is designed with this special shape on the one hand to reduce gear oil and on the other hand also provides sufficient space for the driving shaft 80.

[0051] This is because the area covered by the input shaft 80 in the axial direction, i.e. in the direction of the axis of rotation of the output shaft 40, overlaps with the area covered by the first wall area 25 in the axial direction, but is spaced apart from the area covered by the second wall area 26 in the axial direction.

[0052] The first wall region 25 is radially spaced from the outer wall of the housing part 20. In the intermediate region between the outer wall and the first wall region 25 there is a filling material, in particular air.

[0053] The intermediate area is formed open towards the driven side on the housing part 20 and is thus only covered by the first cover part 1.

[0054] As in Figure 10 As shown, the intermediate region ends at an axial distance and thus before the region covered in the axial direction by the toothed part 45. Therefore, a connecting wall region delimits the intermediate region, wherein the connecting wall region is connected radially inwardly to the first wall region 25 and radially outwardly to the outer wall.

[0055] In contrast, when executing according to the Figures 1 to 5 the intermediate area is axially continuous through the housing part 20.

[0056] Since the gear part Figure 4 radially less extended than in Figure 10, the intermediate region is axially continuous through the housing part 20. Thus, the area covered by the intermediate region 23 in the axial direction encompasses the area covered by the toothed part 45 in the axial direction.

[0057] The first wall region 25 extends at a constant radial distance to a connecting wall region, which extends radially to a further wall region extending axially at a constant radial distance, which is also still radially spaced from the outer wall, but less than the first wall region 25. The intermediate region is therefore covered axially on both sides by a respective cover part 1.

[0058] The second wall region 26 extends at a constant radial distance to a connecting wall region, which extends radially to another wall region extending axially at a constant radial distance, which is also still radially spaced from the outer wall, but less than the second wall region 26, and is held at one or more circumferential points by a web region which is connected both to the outer wall and to this further wall region extending axially at a constant radial distance. The intermediate region between the outer wall and the second wall region 26 is therefore also axially continuous and is thus covered axially on both sides by the respective cover part 1.

[0059] Advantageously, the first ring region 5 of the first cover part 1 is received in the first wall region 26 and thus supported, so that the first bearing 41 and the first sealing ring 43 are held stably, in particular in the case of transverse forces introduced by the engaged gears or by the load.

[0060] The toothed part is arranged closer to the second bearing 46 than to the first bearing 41. In addition, the second bearing 41 is accommodated in the first ring area 5 of the second cover part 1, whereby there is no support by the housing part 20.

[0061] In further embodiments according to the invention, a filler material is arranged in the intermediate region, which stores a lubricant and releases it into the gearbox interior during idle time. For this purpose, the first and / or second wall region (25, 26) or the connecting wall region has continuous recesses. In this way, only a very small amount of lubricant is required for the gearbox interior during assembly, since lubricant is supplied from the intermediate space during operation, particularly to the points to be lubricated, such as bearings and meshing gears. Temperature fluctuations that occur between idle times and operating times promote the release of lubricant into the gearbox interior. List of reference symbols

[0062] 1 Cover part 2 Seat for first bearing 41 3 Seat for sealing ring 4 Seat for sealing ring 5 First ring area 6 Second ring area 20 Housing part 21 Seat for sealing ring 22 Seat for sealing ring 23 Axially continuous recess 24 Transition area, in particular step or smooth transition area 25 First wall area 26 Second wall area 27 Threaded hole for connecting screw 28 Threaded hole for connecting a device to be driven 40 Output shaft 41 First bearing 42 Shaft sealing ring 43 First sealing ring 44 Second sealing ring 45 Toothed part 46 Second bearing 50 Connecting screw

Claims

1. Gear unit comprising a housing part (20), a first cover part (1) and a second cover part, wherein a shaft (40) is rotatably mounted via a first and a second bearing (41, 46), in particular wherein a toothed part (45) is connected to the shaft (40) for conjoint rotation, wherein the first bearing (41) is accommodated in a first annular region (5) of the first cover part, in particular on the radial inner side of a first annular region (5) of the first cover part, wherein the first annular region (5) is inserted and / or accommodated in a recess (23) formed in an annular wall of the housing part (20), wherein the annular wall comprises a first wall region (25), a second wall region (26) and a transition region (24), wherein the first wall region (25) is arranged in a first circumferential angle range, wherein the second wall region (26) is arranged in a second circumferential angle range, which is spaced apart from the first circumferential angle range, wherein the transition region (24) connects the two wall regions (25, 26), i.e. in particular covers in the circumferential direction one of the two circumferential angle ranges arranged between the first and the second circumferential angle range, wherein the area covered by the first wall region (25) in the axial direction includes the area covered by the second wall region (26) in the axial direction, wherein the axial direction is oriented parallel to the direction of the axis of rotation of the shaft (40), wherein the first wall region (25) is radially spaced apart from an outer wall of the housing part (20), and wherein the outer wall of the housing part (20) radially surrounds the first wall region (25) in the area jointly covered by the outer wall and the first wall region (25) in the axial direction, wherein the second wall region (26) is radially spaced apart from the outer wall of the housing part (20), and wherein the outer wall of the housing part (20) radially surrounds the second wall region (26) in the area jointly covered by the outer wall and the second wall region (26) in the axial direction, characterized in that the first wall region (25) extends further than the second wall region (26) in the axial direction from the axial end of the annular wall, wherein the first annular region (5) on the first cover part (1) projects into the interior of the gear unit in the axial direction, the first wall region (25), at the axial end region thereof facing toward the toothed part (45) connected to the shaft (40) for conjoint rotation, is connected to the outer wall via a connecting wall region, wherein the connecting wall region extends radially, wherein the area covered by the first wall region (25) in the axial direction is spaced apart from the area covered by the toothed part (45) in the axial direction, wherein the transition region (24) is configured to be stepped or smooth, i.e. in particular continuously differentiable, wherein the first wall region (25) has an axial extent that is independent of the circumferential angle, i.e. in particular constant, and the second wall region (26) has an axial extent that is independent of the circumferential angle, i.e. in particular constant, wherein the axial extent of the transition region (24) is a step function or a smooth function of the circumferential angle, wherein the first wall region (25) extends at a constant radial spacing until the connecting wall region, which extends radially until a further wall region, which further wall region extends axially at a constant radial spacing and is also still radially spaced apart from the outer wall, but by a smaller spacing than the first wall region (25), wherein the second wall region (26) extends at a constant radial spacing until the connecting wall region, which extends radially until a further wall region, which further wall region extends axially at a constant radial spacing and is also still radially spaced apart from the outer wall, but by a smaller spacing than the second wall region (26), and is supported at one or more points on the circumference by a web region which is connected both to the outer wall and to this further wall region extending axially at a constant radial spacing.

2. Gear unit according to claim 1, characterized in that the intermediate area between the outer wall and the first wall region (25) is configured to pass axially all the way through the housing part (20), and / or in that an intermediate area between the outer wall and the second wall region (26) is configured to pass axially all the way through the housing part (20).

3. Gear unit according to any one of the preceding claims, characterized in that the intermediate area between the outer wall and the first wall region (25) consists of air or a filling material, and / or in that the intermediate area between the outer wall and the second wall region (26) consists of air or a filling material.

4. Gear unit according to any one of the preceding claims, characterized in that the filling material contains a lubricant which can be directed to lubrication points, in particular bearings or a teeth meshing region, of the gear unit.

5. Gear unit according to any one of the preceding claims, characterized in that the area covered by the first wall region (25) in the axial direction overlaps with the area covered by an input shaft (40) in the axial direction.

6. Gear unit according to any one of the preceding claims, characterized in that the input shaft (40) is spaced apart in the axial direction from the first wall region (25).

7. Gear unit according to any one of the preceding claims, characterized in that the first cover part (1) is configured to be identical to the second cover part and / or to have the same structure as the latter.

8. Gear unit according to any one of the preceding claims, characterized in that the radial spacing area covered by the input shaft (40) includes the radial spacing area covered by the first wall region (25), and / or in that the radial spacing area covered by the input shaft (40) includes the radial spacing area covered by the second wall region (26).

9. Gear unit according to any one of the preceding claims, characterized in that a second bearing (46) is accommodated by the first annular region (5) of the second cover part, in particular on the radial inner side thereof, and / or in that the toothed part (45) is arranged closer to the second bearing (46) than to the first bearing (41).

10. Gear unit according to any one of the preceding claims, characterized in that the toothed part (45) meshes with a toothing of an input shaft (40) or with a toothing of a part connected to the input shaft (40), wherein the axis of rotation of the input shaft (40) is oriented perpendicular to the axis of rotation of the toothed part (45), in particular wherein the axis of rotation of the toothed part (45) is spaced apart from the axis of rotation of the input shaft (40).