Semi-direct-drive transmission device for vertical mill

Abstract

The invention relates to a semi-direct-drive transmission device for a vertical mill, which comprises an integral box body (10), and a dividing wall (46) extending inwards from the box body divides the internal space of the box body into an upper planetary transmission area (14) and a lower motor area (12); a motor (16); a flange (30) mounted to the upper end of the case (10) to collectively define a planetary transmission zone (14); the planetary transmission assembly (20) is contained in the planetary transmission area and comprises a transmission shaft (62), a sun gear, a planet carrier (68) integrally extending into the planetary transmission area from the flange, an inner gear ring (66) and a planet gear (64); the thrust pad bearing (50) is arranged on the radial outer face of the inner gear ring, and the upper side and the lower side of the thrust pad bearing are connected with the flange and a supporting part (48) extending inwards from the box body into the planetary transmission area respectively; and a sliding bearing (40) via which a lower end portion (74) of the planet carrier is supported on the support portion (48).

Description

Technical Field

[0001] The present application relates to a semi-direct drive (motor) transmission device for a vertical mill, and the vertical mill is particularly used in power plants, cement, steel, mining, metallurgy, coal chemical industry and other applications. Background Art

[0002] In the vertical mill industry, semi-direct drive transmission devices are used to replace the previous direct drive transmission devices, which to a certain extent improves the shortcomings of low transmission efficiency, large footprint, and inconvenient operation and maintenance.

[0003] However, many semi-direct drive transmission devices use a structure in which the motor housing and the planetary gearbox are separated and then connected together, which is complex in structure and assembly. The complex structure makes the size of the transmission device itself, especially the axial size, larger, and also makes it difficult to make the interface structure and size of the transmission device as a whole consistent with other parts of the vertical mill, and the versatility is poor. In addition, the moving parts in the planetary gearbox are lubricated with lubricating oil, and the bearings supporting the motor shaft are lubricated with grease. The current structure makes it difficult to effectively isolate the grease and oil, and the lubricating oil in the gearbox enters the motor housing and mixes with the grease, which will cause motor failure. Summary of the invention

[0004] The purpose of the present application is to provide a semi-direct drive (motor) transmission device with a simplified structure and solving many other problems at the same time.

[0005] This object is achieved by a semi-direct drive transmission device for a vertical mill. The semi-direct drive transmission device of the present application comprises:

[0006] An integral housing is placed vertically and defines a cylindrical internal space, wherein a partition wall extending inwardly from the housing into the internal space divides the internal space into an upper planetary transmission area and a lower motor area;

[0007] A motor housed in the motor area, comprising a rotor shaft extending in a vertical direction;

[0008] a flange mounted to the upper end of the housing to define the planetary transmission area together with the housing;

[0009] A planetary transmission assembly accommodated in the planetary transmission area, comprising: a transmission shaft coaxially arranged with the rotor shaft and directly engaged with the rotor shaft so as to be driven and rotated synchronously therewith, a sun gear formed integrally with the transmission shaft or coaxially fixed thereto, a planet carrier integrally extending from a flange into the planetary transmission area, an inner gear ring coaxially arranged with the planet carrier, and planetary gears simultaneously engaged with the inner teeth of the inner gear ring and the outer teeth of the sun gear;

[0010] a thrust pad bearing arranged radially outside the inner gear ring, the upper side and the lower side of the thrust pad bearing respectively engaging the flange and a support portion extending inwardly from the housing into the planetary transmission area; and

[0011] A sliding bearing, wherein the lower end of the planet carrier is supported on the support portion via the sliding bearing.

[0012] In one embodiment, the rotor shaft is rotatably supported by a first bearing located near its upper end and a second bearing located near its lower end, and a bearing bushing engaging a bearing outer ring of the first bearing from a radially outer side engages with the partition wall to separate the motor area and the planetary transmission area.

[0013] In one embodiment, the first bearing is a limit bearing that provides a vertical limit for the rotor shaft, the second bearing is a thrust bearing that provides an upward thrust for the rotor shaft in the vertical direction, and the rotor shaft is also rotatably supported by a rolling bearing located above the thrust bearing.

[0014] In one embodiment, the semi-direct drive transmission device also includes an upper bearing end cover and a lower bearing end cover respectively engaged with the upper side and the lower side of the bearing outer ring of the first bearing, and the upper bearing end cover and the lower bearing end cover are respectively directly or indirectly engaged to the outer circumferential surface of the rotor shaft in a fluid-tight manner.

[0015] In one embodiment, the semi-direct drive transmission device also includes: an upper shaft ring fastened to the rotor shaft on the upper side of the upper bearing end cover, which extends radially outward to the radial outside of at least one of the upper bearing end cover and the bearing bushing and is bent downward to cover at least a portion of the at least one; and a lower shaft ring fastened to the rotor shaft on the lower side of the lower bearing end cover, which extends radially outward to the radial outside of at least one of the lower bearing end cover and the bearing bushing and is bent upward.

[0016] In one embodiment, the upper bearing end cover and the lower bearing end cover are respectively gap-engaged with the bearing outer ring, and a sealing member is provided between the upper bearing end cover and the bearing outer ring.

[0017] In one embodiment, the transmission shaft and the rotor shaft are engaged by a crowned tooth spline so that the rotor shaft can drive the transmission shaft to rotate.

[0018] In one embodiment, the drive shaft and the rotor shaft have spherical end surfaces that engage each other.

[0019] In one embodiment, the flange includes: a recessed area formed by recessing from the upper end surface of the output flange and in which the upper end of the pin supporting the planetary gear is exposed, and a central space accommodating the sun gear, wherein the recessed area and the central space are fluidically connected via an internal fluid channel passing through the output flange and / or the planetary carrier. In one embodiment, the semi-direct drive transmission device includes: a lubrication passage for introducing lubricating oil from outside the housing to the sliding bearing in the housing at the height of the sliding bearing, guiding the lubricating oil after passing through the sliding bearing and upward to the recessed area, guiding the lubricating oil in the recessed area to the central space, and guiding the lubricating oil in the recessed area to the bearing supporting the planetary gear via a pin channel formed in the pin.

[0020] In one embodiment, the invention further comprises a pipeline for guiding the lubricating oil in the recessed area into the central space, wherein the pipeline comprises a nozzle for spraying the lubricating oil toward the sun gear.

[0021] In one embodiment, the pin is formed with a pin channel for guiding lubricating oil in the recessed area to the bearings on the supporting planetary gear.

[0022] In one embodiment, the semi-direct drive transmission further comprises another lubrication passage for introducing lubricating oil from outside the housing into the housing at the level of the thrust pad bearing.

[0023] In one embodiment, the semi-direct drive transmission device further includes an oil return port formed on the housing, and the lubricating oil in the first lubrication passage and the second lubrication passage are both discharged from the housing through the oil return port via the oil return area located below the planetary carrier.

[0024] In one embodiment, a lower surface of the support portion of the housing partially defines the oil return area, and the lower surface is lower than a lowermost surface of the downwardly bent portion of the upper collar.

[0025] The semi-direct drive transmission device for vertical mill of the present application adopts an integrated housing that accommodates the motor structure and the planetary transmission structure, and the planetary carrier and flange of the planetary transmission structure are formed integrally. First, this reduces the number of parts of the transmission device, reduces the complexity of the planetary transmission structure and the housing structure, reduces the processing and assembly costs, and has the advantage of cost control. Secondly, the use of an integrated housing and an integrated planetary carrier and flange makes the structure of the transmission device as compact as possible, thereby minimizing the size of the entire device, especially in terms of axial size or axial height, which can save a lot of space. The transmission device can also achieve the same interface size as the existing interface system, realizing lossless replacement, which provides the widest versatility.

[0026] The present application also provides other technical advantages: compared with the traditional sealing structure, the present application achieves a reliable grease separation effect while using the same housing to provide the motor area and the planetary transmission area by adopting a structure that combines a shaft seal, an oil retaining ring and an oil receiving ring. Specifically, the lubricating oil in the planetary transmission area is perfectly isolated from the grease used to lubricate the bearings of the rotor shaft, thereby ensuring the reliability of the seal during long-term operation of the vertical mill. BRIEF DESCRIPTION OF THE DRAWINGS

[0027] Figure 1 It is a structural diagram of a semi-direct drive transmission device for a vertical mill constructed according to the principle of the present application. DETAILED DESCRIPTION

[0028] The semi-direct drive (motor) transmission device of the present application is described in detail below with reference to the accompanying drawings. It is particularly suitable for vertical mills in which the rotor shaft of the motor and the transmission shaft of the planetary transmission mechanism are coaxially arranged, and is more particularly suitable for heavy-load vertical mills in power plants, cement, and steel applications.

[0029] refer to Figure 1 In general, the semi-direct drive transmission device for vertical mill of the present application includes an integrated housing 10, which defines a motor area 12 and a planetary transmission area 14 that are connected to each other. The motor 16 and the planetary transmission structure 20 are respectively accommodated in the motor area 12 and the planetary transmission area 14 of the integrated housing 10. The housing bottom plate 18 and the flange 30 are respectively installed at the upper end and the lower end of the integrated housing 10, respectively encapsulating the motor 16 and the planetary transmission structure 20 in the integrated housing 10.

[0030] The motor 16 includes a rotor shaft 22 having a central axis X, which extends in an axial direction. As shown in the figure, in a vertical mill application, the axial direction is the vertical direction, and the transmission device is placed vertically. Therefore, in this application, the terms axial direction and vertical direction can be used interchangeably, and the directional terms "upper" and "lower", "top" and "bottom" all have their commonly understood meanings, and can also be understood by referring to the orientation of the accompanying drawings.

[0031] The motor 16 also includes a rotor and a stator and other components arranged radially outward from the rotor shaft in a radial direction perpendicular to the axial direction. These structures are not the focus of this application and are not described in detail here. They are only schematically shown by dotted lines in the drawings. The rotor shaft 22 is supported by bearings at both ends of the axial direction and can rotate around the central axis X. Specifically, as shown in the figure, a limiting bearing 24 for providing a limiting effect on the rotor shaft 22 in the vertical direction (especially in the downward direction) is arranged and supported at the upper end of the rotor shaft 22, specifically around the outer peripheral surface of the upper end of the rotor shaft 22. As an example, the limiting bearing 24 can be a deep groove ball bearing; a rolling bearing 26 (such as a NU bearing) and a thrust bearing (such as a spherical roller thrust bearing) 28 are arranged and supported at the lower end of the rotor shaft 22, wherein the rolling bearing 26 is arranged around its outer peripheral surface near the lower end of the rotor shaft 22; the thrust bearing 28 is closer to the lower end of the rotor shaft 22 than the rolling bearing 26, and is set against the shoulder 25 of the rotor shaft 22 so as to provide an upward supporting force to the rotor shaft 22. This bearing combination arrangement is very advantageous in that the limiting ball bearing 24 and the rolling bearing 26 can bear the unilateral magnetic pull, and the thrust bearing 28 bears the weight of the rotor assembly of the motor 16. In addition, this bearing combination arrangement can enable each bearing to operate under more ideal working conditions with lower heat generation temperature, which has the advantage of improving the operating reliability of the entire machine.

[0032] At the lower end of the rotor shaft 22, the bearings 26 and 28 of the rotor shaft 22 are fixed to the housing bottom plate 18 by at least one bearing end cover. For example, in the illustrated example, the bearing end cover 21 abuts against and axially positions the rolling bearing 26 from the axial upper side of the rolling bearing 26, and the bearing end cover 23 is arranged below the rotor shaft 22, including a portion that pushes against or positions the bearing outer ring of the rolling bearing 26 from the radial outer side and a portion that pushes against or supports the bearing outer ring of the thrust bearing 28 from below. The bearing end cover 21 and the bearing end cover 23 can be fastened directly to the housing bottom plate 18, or fastened to the housing bottom plate 18 via an intermediate member 27. The housing bottom plate 18 is fixed to the integrated housing 10 by any known means in the art, such as bolt connection.

[0033] The housing 10 includes a lower housing wall 42 connected to the housing bottom plate 18 to define the motor area 12, an upper housing wall 44 integrally formed with the lower housing wall 42 and engaged with the flange 30 to define the planetary transmission area 14, and a partition wall 46 extending radially inwardly from the connection between the lower housing wall 42 and the upper housing wall 44 to separate the motor area 12 and the planetary transmission area 14. The bearing bushing 52 radially inwardly pushed against the outer ring of the bearing of the limit bearing 24 from the radial outer side thereof is supported on the partition wall 46 to physically separate the motor area 12 and the planetary transmission area 14.

[0034] The upper bearing end cap 54 and the lower bearing end cap 56 are mounted on the rotor shaft 22 and engage the bearing outer ring of the limit bearing 24 from the upper side and the lower side of the limit bearing 24, respectively. The upper bearing end cap 54 and the lower bearing end cap 56 are fastened to the bearing bushing 52 and thus do not rotate with the rotor shaft 22.

[0035] The stationary upper bearing end cover 54 is fluid-tightly coupled to the outer circumference of the rotatable rotor shaft 22 through a seal (or upper shaft seal) 33. An upper shaft ring (or upper oil retaining ring) 57 is provided on the upper side of the upper bearing end cover 54. In the vertical direction, the upper shaft ring 57 covers the gap between the radial inner circumference of the upper bearing end cover 54 and the outer circumference of the rotor shaft 22 from the upper side to prevent the lubricating oil of the planetary transmission area 14 from entering the gap. The upper shaft ring 57 extends radially outward beyond the upper bearing end cover 54 or at least a portion thereof, and then bends downward to prevent the lubricating oil from entering between the upper shaft ring 57 and the upper bearing end cover 54.

[0036] The stationary lower bearing end cover 56 is fluid-sealed to the outer circumference of the rotor shaft 22 via the lower seal (or lower shaft seal) 37, or as shown in the figure, is fluid-sealed to the corresponding outer circumference of the intermediate shaft ring 59 that is fastened to the rotor shaft 22 and rotates therewith. The lower shaft ring (or lower oil retaining ring) 58 is arranged on the lower side of the lower bearing end cover 56, which extends radially outward beyond the lower bearing end cover 56 and bends upward. Optionally, but not necessarily, as shown in the figure, the lower shaft ring 58 is further bent radially inward toward the lower bearing end cover 56 after being bent upward.

[0037] Thus, the upper bearing end cover 54, the lower bearing end cover 56, the bearing bushing 52 and the rotor shaft 22 define a grease containing area for containing grease for lubricating the stop bearing 24, and effectively prevent the lubricating oil from the planetary transmission area 14 from entering the grease containing area. The lower shaft ring 58 is arranged on the lower side of the stop bearing 24, and is used to further ensure that the lubricating oil accidentally leaked from the planetary transmission area 14 into the stop bearing 24 will not enter the motor area 12.

[0038] In addition, the upper bearing end cover 54 is sealed to the upper side of the bearing outer ring of the limit bearing 24 through the seal 39. At the same time, gaps are provided between the upper bearing end cover 54 and the lower bearing end cover 56 and the upper and lower sides of the bearing outer ring of the limit bearing 24 to form gap engagement, so as to reduce the impact of the rotor shaft 22 on the bearing when it expands and contracts due to temperature changes. The bearing 24 can also be replaced without disassembling the rotor shaft 22, which is convenient for maintenance.

[0039] The planetary transmission structure 20 is accommodated in the planetary transmission area 14, and includes a transmission shaft 62 coaxially engaged with the rotor shaft 22 and driven to rotate therewith, as shown in the figure, a sun gear (in the present application, the transmission shaft 62 is also referred to as the sun gear shaft 62) formed integrally with the transmission shaft 62 or otherwise fastened to the transmission shaft 62 to rotate therewith, and at least one planetary gear 64 is arranged to mesh with the external teeth of the sun gear shaft 62 and the internal teeth of the inner gear ring 66. As shown in the figure, the planetary gear 64 is supported in a pin shaft hole 61 formed on the planetary carrier 68 through a pin shaft 65. The planetary carrier 68 is formed integrally with the flange 30 and extends axially downward from the flange 30.

[0040] The transmission shaft 62 and the rotor shaft 22 can be engaged by a spline, preferably a drum-shaped tooth spline, so that the rotation of the rotor shaft 22 can cause the transmission shaft 62 or the sun gear to rotate. The transmission shaft 62 and the rotor shaft 22 include spherical end surfaces (at 51 in the figure) that engage with each other. The drum-shaped tooth spline engagement structure allows the sun gear or the transmission shaft 62 to have a certain amount of swing relative to the rotor shaft 22, and has the ability to balance the load of the planetary transmission. This structure is also better than the current integral gear shaft structure, because the transmission shaft 62 and the rotor shaft 22 of this structure can be made of different materials, with high performance and cost savings.

[0041] The planet carrier 68 includes a cylindrical frame body 72 extending axially downward from the flange 30 and a lower end portion 74 extending radially from the lower end of the cylindrical frame body 72 and including a radially inwardly extending portion and a radially outwardly extending portion. The radially outwardly extending portion of the lower end portion 74 is located below the planetary gear 64 and is supported on a support portion 48 protruding radially inwardly from the upper housing wall 44 into the planetary transmission area 14 via a sliding bearing 40. In the vertical direction, the thrust pad bearing 50 is arranged between the output flange 30 and the support portion 48 of the housing 10, and is used to transfer the load borne by the flange 30 to the housing 10 during the operation of the vertical mill.

[0042] The flange 30 and the planet carrier 68 (cylindrical carrier body 72 thereof) include a central hole 71 coaxial with the transmission shaft 62, the upper end of the transmission shaft (or the sun gear shaft of the present application) 62 is exposed to the central hole 71, and the inner diameter of the central hole 71 can be larger than the outer diameter of the outer teeth of the sun gear (shaft) to install the sun gear. The pin shaft hole 61 is radially offset outward from the central hole 71, and the planet gear 64 is rotatably supported in the pin shaft hole 61 through the bearing 67.

[0043] Advantageously, in order to provide sufficient oil lubrication for the thrust bearing 50 and the sliding bearing 40, the semi-direct drive transmission device of the present application includes two lubrication passages, a first lubrication passage P1 and a second lubrication passage P2, for example, both of which enter the housing 10 from a lubrication oil supply source S outside the mill.

[0044] The first lubrication passage P1 may include: a first entry passage section P11 extending from the outside of the housing 10 through the housing 10 to the thrust bearing 50 at a height substantially equal to the thrust pad bearing 50, for example, it may extend horizontally or substantially horizontally in the housing 10 as shown. Afterwards, the lubricating oil reaches the teeth of the inner gear ring 66 through the gap between the upper end of the inner gear ring 66 and the flange 30 after passing through the thrust pad bearing 50, lubricates the teeth of the inner gear ring 66 and the planetary gear 64 that mesh with each other, and then reaches the bearing 67 that supports the planetary gear 64.

[0045] In addition to the above-mentioned first lubrication passage P1, the semi-direct drive transmission device of the present application also includes a second lubrication passage P2, which may include: a second entry passage section P21 extending from the outside of the housing 10 through the housing 10, specifically through the support portion 48 of the housing 10 to reach the sliding bearing 40, for example, it may extend horizontally or approximately horizontally in the housing 10 as shown in the figure, for example, the passage section P21 is located below the passage section P11, preferably at approximately the height of the sliding bearing 40; a bearing passage section P22 extending laterally, for example horizontally, through the sliding bearing 40; and a bearing passage section P22 extending upward, or obliquely upward, or first radially after passing through the sliding bearing 40. An upward channel section P23 extending horizontally inward and then vertically upward through the flange 30 to reach the recessed space 82 of the flange 30; a downward channel section P24 extending through the flange 30 and / or the planet carrier 68 and extending from the recessed space 82 of the flange 30 to the central space 84 of the flange 30 to guide the lubricating oil in the recessed space 82 to the sun gear (shaft) 62, which preferably extends vertically or substantially vertically in the flange 30 as shown; and a pin shaft channel section P25 extending through the pin shaft 65 to guide the lubricating oil in the recessed space 82 to the bearing 67 supporting the pin shaft 65, which may include one or more sections connected to each other. Among them, the recessed space 82 is a recessed portion formed on the upper end surface 81 of the flange 30, such as an annular recessed portion, which can be, but not necessarily, separated from the central hole 71 by the annular portion 85 as shown. In some embodiments, the annular portion 85 can be omitted, and the recessed space 82 can be a circular recessed area.

[0046] The provision of the second lubrication passage P2 achieves sufficient lubrication of the sliding bearing 40, sufficient lubrication of the bearing 67 of the planetary gear 64, and sufficient lubrication of the sun gear shaft 62. Optionally, but not necessarily, a conduit 86 for guiding lubricating oil extends from the recessed space 82 to the central space 84 and includes one or more nozzles 88 for spraying lubricating oil toward the sun gear.

[0047] As described above, the lubricating oil from the first lubricating passage P1 and the second lubricating passage P2 flows downward through the planetary gear 64 and the bearing 67 to the gap 90 between the planetary gear 64 and the bearing 67 and the support portion 48 and the sliding bearing 40 of the housing 10, and enters the oil return area R through the sliding bearing 40. The oil return area R is located below the planetary transmission structure 20, and the upper side of the oil return area R is defined by the lower surface 41 of the support portion 48 of the housing 10 and the planetary transmission structure 20 (specifically, the lowest surface of its planet carrier 68 and the lower surface of the pin 65), and the lower side is defined by the partition wall 46 and the bearing bushing 52 of the housing 10, and includes the oil discharge port O formed on the housing 10. The lowest surface of the upper side defining the oil return area R is the lower surface 41 of the support portion 48, which is preferably set to be higher than the lowest surface of the upper collar 57, so that the liquid level of the oil discharge port O does not substantially rise to a position where it can enter between the upper collar 57 and the upper bearing end cover 54. In addition, for the same purpose, preferably, at least most of the oil discharge port O, preferably the entire oil discharge port O is lower than the lowest surface of the upper shaft ring 57. This arrangement prevents the lubricating oil used to lubricate the planetary transmission structure 20 from entering the grease space used to lubricate the limit bearing 24 supporting the rotor shaft 22 through the gap between the upper shaft ring 57 and the upper bearing end cover 54 to the greatest extent, thereby effectively avoiding the mixing of the lubricating oil and the grease.

[0048] The structure of the semi-direct drive transmission device of the present application is described in detail above with reference to the accompanying drawings. It can be seen from the above that the semi-direct drive transmission device of the present application adopts an integrated housing 10 that can provide both the motor area and the planetary transmission area, and adopts an integrated structure of a planetary carrier and a flange, which reduces the number of planetary transmission parts, simplifies the structure of the device, reduces the manufacturing and assembly costs, and minimizes the external volume and occupied space of the device, especially the axial dimension of the device is minimized, reducing the total weight of the device. The device has the widest versatility. In addition, the minimization of the axial dimension of the planetary transmission structure is also beneficial to improving the efficiency of the motor.

[0049] The present application provides two lubrication passages, which provide sufficient lubrication for the thrust bearing and the sliding bearing respectively. The second lubrication passage passes through the interior of the sliding bearing to achieve dynamic pressure lubrication of the sliding bearing itself. The second lubrication passage also provides forced lubrication of the planetary transmission components to ensure reliable operation of the transmission device.

[0050] In the semi-direct drive transmission device of the present application, the working load borne by the flange 30 is transmitted to the housing in the axial direction through the thrust bearing 50, and is also transmitted to the housing in the radial direction through the radial engagement of the planetary carrier and the sliding bearing that are integral with the flange.

[0051] The embodiments of the present invention are described in detail above in conjunction with the drawings of the specification, but those skilled in the art should understand that the above embodiment is only an implementation of the present invention and does not limit the protection scope of the present invention. On the contrary, any improvement or modification based on the content of the present invention should be considered within the protection scope of the present invention. The protection scope of this application is limited only by the claims.

Claims

1. A semi-direct drive transmission device for a vertical mill, comprising: An integrated housing (10) is placed vertically and defines a cylindrical internal space, wherein a partition wall (46) extending inwardly from the housing into the internal space divides the internal space into an upper planetary transmission area (14) and a lower motor area (12); The motor (16) is housed in the motor area (12), and includes a rotor shaft (22) extending in a vertical direction: A flange (30) mounted to the upper end of the housing (10) to define the planetary transmission area (14) together with the housing; A planetary transmission assembly (20) housed in a planetary transmission area (14), comprising: a transmission shaft (62) coaxially arranged with the rotor shaft (22) and directly engaged with the rotor shaft (22) so as to be driven and rotated synchronously therewith, a sun gear formed integrally with the transmission shaft or coaxially fixed thereto, a planet carrier (68) integrally extending from a flange (30) into the planetary transmission area (14), an inner gear ring (66) coaxially arranged with the planet carrier, and a planetary gear (64) simultaneously engaged with the inner teeth of the inner gear ring and the outer teeth of the sun gear; a thrust bearing (50) disposed radially outside the inner gear ring, the upper side and the lower side of the thrust bearing respectively engaging the output flange (30) and a support portion (48) extending inwardly from the housing into the planetary transmission area (14); and A sliding bearing (40), wherein the lower end portion (74) of the planet carrier (68) is supported on the support portion (48) via the sliding bearing.

2. The semi-direct drive transmission device according to claim 1, wherein: The rotor shaft (22) is rotatably supported by a first bearing located near its upper end and a second bearing located near its lower end, and a bearing bushing (52) engaging the bearing outer ring of the first bearing from the radial outside is engaged with the partition wall (46) to separate the motor area (12) and the planetary transmission area (14).

3. The semi-direct drive transmission device according to claim 2, wherein: The first bearing is a limit bearing (24) for limiting the rotor shaft in the vertical direction, the second bearing is a thrust bearing (28) for providing an upward thrust in the vertical direction to the rotor shaft, and the rotor shaft is rotatably supported by a rolling bearing (26) located above the thrust bearing (28).

4. The semi-direct drive transmission device according to claim 2 further includes an upper bearing end cover (54) and a lower bearing end cover (56) respectively engaged with the upper side and the lower side of the bearing outer ring of the first bearing, and the upper bearing end cover and the lower bearing end cover are respectively directly or indirectly engaged to the outer circumferential surface of the rotor shaft in a fluid-tight manner.

5. The semi-direct drive transmission device according to claim 4, further comprising: An upper shaft ring (57) is fastened to the rotor shaft (22) on the upper side of the upper bearing end cover (54), extending radially outward to the radial outer side of at least one of the upper bearing end cover and the bearing bushing and bending downward to cover at least a portion of the at least one; and a lower shaft ring (58) is fastened to the rotor shaft (22) on the lower side of the lower bearing end cover (56), extending radially outward to the radial outer side of at least one of the lower bearing end cover and the bearing bushing and bending upward.

6. The semi-direct drive transmission device according to claim 4, wherein: The upper bearing end cover (54) and the lower bearing end cover (56) are respectively gap-engaged with the bearing outer ring, and a sealing component (39) is provided between the upper bearing end cover (54) and the bearing outer ring.

7. The semi-direct drive transmission device according to any one of claims 1 to 6, wherein: The transmission shaft (62) and the rotor shaft (22) are engaged via a crowned tooth spline so that the rotor shaft can drive the transmission shaft to rotate.

8. The semi-direct drive transmission device according to claim 7, wherein: The transmission shaft (62) and the rotor shaft (22) have spherical end surfaces that engage with each other.

9. The semi-direct drive transmission according to any one of claims 4 to 6, wherein: The flange (30) includes: a recessed area (82) formed by being recessed from an upper end surface (81) of the output flange and in which an upper end of a pin shaft (65) supporting the planetary gear (64) is exposed, and a central space (84) accommodating the sun gear, wherein the recessed area and the central space are in fluid communication via an internal fluid passage (P24) passing through the output flange and / or the planetary carrier; and The semi-direct drive transmission device comprises a lubrication passage (P2) for introducing lubricating oil from outside the housing (10) to the sliding bearing (40) inside the housing (10), guiding the lubricating oil upward to the recessed area (82) after passing through the sliding bearing (40), guiding the lubricating oil in the recessed area (82) into the central space (84), and guiding the lubricating oil in the recessed area (82) to the bearing (67) on the supporting planetary gear (64) via a pin shaft passage (P25) formed in the pin shaft (65).

10. The semi-direct drive transmission according to claim 9, further comprising a pipe (86) for guiding the lubricating oil in the recessed area (82) to the central space (84), the pipe (86) comprising a nozzle (88) for spraying the lubricating oil toward the sun gear.

11. The semi-direct drive transmission according to claim 9, wherein: The pin shaft (65) is formed with a pin shaft passage (P25) for guiding lubricating oil in the recessed area (82) to the bearing (67) on the supporting planetary gear (64).

12. The semi-direct drive transmission device according to claim 11, further comprising another lubrication passage for introducing lubricating oil from outside the housing (10) into the thrust pad bearing inside the housing (10).

13. The semi-direct drive transmission device according to claim 12 further includes an oil return port (O) formed on the housing (10), and the lubricating oil in the first lubrication passage and the second lubrication passage are discharged from the housing (10) from the oil return port (O) via an oil return area (R) located below the planetary carrier (68).

14. The semi-direct drive transmission according to claim 13, wherein: The lower surface (41) of the support portion (48) of the housing partially defines the oil return area (R), and the lower surface is lower than the lowest surface of the downwardly bent portion of the upper collar (57).

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