Gearbox for rail train

Abstract

The present invention discloses a gearbox for an orbital train. The gearbox includes: a box body, a driving shaft, and a driving gear. An installation cavity for accommodating a driven gear is formed inside the box body; the inner end of the driving shaft is provided with the driving gear. The driving shaft obliquely passes through the box body and the driving gear meshes with the driven gear. The driving shaft is installed on the box body through a driving shaft bearing; wherein, the installation cavity includes: an installation cavity top wall, and the installation cavity top wall is configured as an inclined plane that slopes downward towards the driving shaft bearing, so that the lubricating oil splashed onto the installation cavity top wall flows towards the driving shaft bearing. Thus, on the one hand, by setting the installation cavity top wall that slopes downward towards the driving bearing, the lubrication effect on the driving shaft bearing during the forward rotation and reverse rotation of the gearbox can be effectively improved; on the other hand, there is no need to set components such as an oil guiding plate and an oil collecting plate, which can reduce the number of components inside the gearbox, make the structure of the gearbox simpler, and reduce the production cost of the gearbox.

Description

Technical Field

[0001] The present invention relates to the technical field of rail vehicles, and more particularly to a gearbox for a rail train. Background Art

[0002] An aerial rail train is a new type of rail transit mode. Due to the bogie interface requirements, generally, there is an upward angle of 15° to 30° between the driving shaft of the gearbox of the aerial rail vehicle and the horizontal direction. Therefore, it is necessary to guide the lubricating oil to a higher position to lubricate the outer bearing of the driving shaft.

[0003] Among them, the bearing lubrication of the gearbox generally adopts forced lubrication by an oil pump or splash lubrication.

[0004] If the forced lubrication method by an oil pump is adopted, the following deficiencies exist: (1) The traditional oil pump cannot meet the requirement of pumping oil in the same direction during both forward and reverse rotations; (2) The service life of the oil pump is short and cannot meet the overhaul period of the gearbox.

[0005] If the splash lubrication method is adopted, the following deficiencies exist: (1) The lubrication structure design of the box body cannot meet the requirement of maintaining a good lubrication effect during both forward and reverse rotations of the gearbox of the aerial rail vehicle; (2) Structures such as an oil guiding plate and an oil collecting plate are required inside the box body of the gearbox, and there are many components, and the structure is complex.

[0006] That is to say, in the prior art, there are significant differences between the gearboxes of aerial rail trains and those of common rail trains. There is an angle between the driving shaft and the horizontal direction, and the large angle results in a relatively high height of the outer side of the driving shaft, which in turn makes it difficult for the lubricating oil to move to the outer bearing of the driving shaft, and also makes the existing lubrication methods inapplicable to the gearboxes of aerial rail trains. Summary of the Invention

[0007] The present invention aims to at least solve one of the technical problems existing in the prior art. For this purpose, an object of the present invention is to provide a gearbox for a rail train, which has a better lubrication effect on the outer bearing and a simple structure.

[0008] The gearbox for a rail train according to an embodiment of the present invention includes: a box body, a driving shaft, and a driving gear. An installation cavity for accommodating a driven gear is formed inside the box body; a driving gear is provided at the inner end of the driving shaft. The driving shaft obliquely passes through the box body, and the driving gear meshes with the driven gear. The driving shaft is installed on the box body through a driving shaft bearing; wherein, the installation cavity includes: an installation cavity top wall, and the installation cavity top wall is configured as an inclined surface that slopes downward towards the driving shaft bearing, so that the lubricating oil splashed onto the installation cavity top wall flows towards the driving shaft bearing.

[0009] The gearbox for an orbital train according to an embodiment of the present invention, on the one hand, by providing a top wall of the installation cavity that slopes downward toward the active bearing, the lubrication effect on the active shaft bearing during the forward and reverse rotations of the gearbox can be effectively improved; on the other hand, components such as an oil guide plate and an oil collecting plate do not need to be provided, which can reduce the number of components inside the gearbox, make the structure of the gearbox simpler, and reduce the production cost of the gearbox.

[0010] According to some embodiments of the present invention, the included angle between the top wall of the installation cavity and the horizontal plane is 4° - 7°.

[0011] In some embodiments, the minimum distance between the top wall of the installation cavity and the center line of the driven gear is greater than the large end radius of the driven gear by 7 mm - 12 mm.

[0012] Furthermore, the installation cavity further includes: a bottom wall of the installation cavity, a first side wall of the installation cavity away from the active shaft bearing, and a second side wall of the installation cavity close to the active shaft bearing. Both ends of the bottom wall are connected to the top wall of the installation cavity through the first side wall of the installation cavity and the second side wall of the installation cavity respectively.

[0013] Furthermore, the bottom wall of the installation cavity is configured as an arc surface and is concentric with the driven gear.

[0014] Optionally, the diameter of the bottom wall of the installation cavity is greater than the large end diameter of the driven gear by 10 mm - 15 mm.

[0015] In some embodiments, the second side wall of the installation cavity is configured as an arc surface, the second side wall of the installation cavity is tangent to the bottom wall of the installation cavity, and the diameter of the second side wall of the installation cavity is the same as the diameter of the bottom wall of the installation cavity.

[0016] Furthermore, the intersection point between the top wall of the installation cavity and the first side wall of the installation cavity is rounded, and the fillet radius is 35 mm - 45 mm.

[0017] Furthermore, the distance between one end of the top wall of the installation cavity away from the active shaft bearing and the outer side wall opposite to the first side wall of the installation cavity is 8 mm - 12 mm.

[0018] According to some embodiments of the present invention, the minimum distance between the first side wall of the installation cavity and the outer side wall opposite to it is not less than 10 mm.

[0019] Furthermore, an oil guide groove is provided on the second side wall of the installation cavity and is adapted to guide the lubricating oil on the top wall of the installation cavity to the active shaft bearing.

[0020] Furthermore, the extending direction of the oil guide groove forms an included angle of 10° - 20° with the horizontal plane.

[0021] Optionally, an oil guiding convex portion is further provided on the side wall of the second installation cavity, and the distance between the free end of the oil guiding convex portion and the horizontal plane passing through the center line of the driven gear is 120 mm - 130 mm.

[0022] In some embodiments, the width of the oil guiding groove is the same as the width of the installation cavity.

[0023] Further, a bearing seat is provided between the bearing and the box body, an oil collecting groove communicating with the oil guiding groove is provided on the bearing seat, and a lubricating oil inlet for introducing lubricating oil into the main shaft bearing is provided on the bottom wall of the oil collecting groove.

[0024] Further, a first lubricating oil outlet for discharging lubricating oil is further provided on the bearing seat.

[0025] Optionally, a main shaft sleeve is further provided between the main shaft bearing and the main shaft, and the main shaft sleeve is in interference fit with the main shaft.

[0026] According to some embodiments of the present invention, the gearbox further includes: an end cover and a seal. The end cover is provided between the box body; the seal is provided inside the end cover and the seal and the end cover are circumferentially abutted; wherein the seal and the end cover respectively have a first mating surface and a second mating surface facing each other axially. A plurality of radially spaced-apart stop protrusions are provided on the first mating surface, and a plurality of radially spaced-apart stop grooves are provided on the second mating surface. Each stop protrusion is in plug-in fit with the corresponding stop groove.

[0027] Further, the end cover includes: a bottom wall portion and a side wall portion provided on the periphery of the bottom wall portion and extending inward. The inner end surface of the bottom wall portion is configured as the second mating surface; a circumferential abutting portion is provided on the circumferential surface of the seal, the circumferential abutting portion abuts against the side wall portion, and the outer end surface of the seal is configured as the first mating surface.

[0028] Additional aspects and advantages of the present invention will be given in part in the following description, become apparent in part from the following description, or be learned through the practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0029] The above and / or additional aspects and advantages of the present invention will become apparent and be readily understood from the description of the embodiments in conjunction with the following drawings, wherein:

[0030] Figure 1 is a schematic diagram of a gearbox according to an embodiment of the present invention;

[0031] Figure 2 is Figure 1 an enlarged schematic diagram of area A in

[0032] Figure 3 is a schematic view of the housing of a gearbox according to an embodiment of the present invention;

[0033] Figure 4 is a schematic view of a lubrication path of a gearbox according to an embodiment of the present invention (the driven gear rotates forward);

[0034] Figure 5 is another schematic view of a lubrication path of a gearbox according to an embodiment of the present invention (the driven gear rotates in reverse);

[0035] Figure 6 is along Figure 4 a cross-sectional schematic view along the center line B-B;

[0036] Figure 7 is Figure 4 an enlarged schematic view of area C in

[0037] Figure 8 is Figure 7 an enlarged schematic view of area D in

[0038] Reference numerals:

[0039] gearbox 100,

[0040] housing 10, upper housing 10a, lower housing 10b, installation cavity 11, top wall 111 of the installation cavity, bottom wall 112 of the installation cavity, first side wall 113 of the installation cavity, second side wall 114 of the installation cavity, oil guiding groove 12, oil guiding projection 13,

[0041] drive shaft 20, drive gear 30, drive shaft bearing 40, first bearing 40a, second bearing 40b, driven gear 50, bearing seat 60, oil collecting groove 61, lubricating oil inlet 62, first lubricating oil outlet 63, drive shaft sleeve 70, end cover 80, second mating surface 81, stop groove 82, bottom wall portion 83, side wall portion 84, second lubricating oil outlet 841, seal 90, first mating surface 91, stop projection 92, circumferential stop portion 93. Detailed description of the embodiments

[0042] The embodiments of the present invention will be described in detail below. The examples of the embodiments are shown in the drawings, in which the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the drawings are exemplary and are only used to explain the present invention and should not be construed as a limitation of the present invention.

[0043] The following refers to Figures 1-8 to describe the gearbox 100 for a rail train according to an embodiment of the present invention.

[0044] AsFigures 1-8 As shown in Figures 1-8 , the gearbox 100 for an orbital train according to an embodiment of the present invention includes: a housing 10, a driving shaft 20, and a driving gear 30.

[0045] Among them, an installation cavity 11 for accommodating a driven gear 50 is formed inside the housing 10; a driving gear 30 is provided at the inner end of the driving shaft 20. The driving shaft 20 obliquely passes through the housing 10 and the driving gear 30 meshes with the driven gear 50. The driving shaft 20 is installed on the housing 10 through a driving shaft bearing 40. The installation cavity 11 includes: an installation cavity top wall 111, and the installation cavity top wall 111 is configured as an inclined surface that slopes downward toward the driving shaft bearing 40, so that the lubricating oil splashed onto the installation cavity top wall 111 flows toward the driving shaft bearing 40.

[0046] Specifically, in order to meet the interface requirements of the bogie interface on the track of the orbital train, it is necessary to form an angle of 15 - 30° between the driving shaft 20 of the gearbox 100 and the horizontal direction (that is, the driving shaft 20 obliquely passes through the housing 10 and the driving gear 30 meshes with the driven gear 50). This will increase the height of the driving shaft bearing 40 of the driving shaft 20, thereby increasing the lubrication difficulty of the driving shaft bearing 40. Furthermore, the installation cavity top wall 111 is set as an inclined surface that slopes downward toward the driving shaft bearing 40, so that when the driven gear 50 rotates forward or backward, the lubricating oil splashed onto the installation cavity top wall 111 can adhere to this inclined surface and flow toward the driving shaft bearing 40, so that the driving shaft bearing 40 is fully lubricated.

[0047] It should be noted that the forward rotation of the driven gear 50 means that the driven gear 50 rotates clockwise; the reverse rotation of the driven gear 50 means that the driven gear 50 rotates counterclockwise.

[0048] For the gearbox 100 for an orbital train according to an embodiment of the present invention, on the one hand, by setting the installation cavity top wall 111 that slopes downward toward the driving shaft 20 bearing, the lubrication effect on the driving shaft bearing 40 during the forward and reverse rotations of the gearbox 100 can be effectively improved; on the other hand, there is no need to set up components such as an oil guiding plate and an oil collecting plate, which can reduce the number of components inside the gearbox 100, make the structure of the gearbox 100 simpler, and reduce the production cost of the gearbox 100.

[0049] It can be understood that the driving shaft bearing 40 includes a first bearing 40a and a second bearing 40b. The first bearing 40a and the second bearing 40b are spaced apart in the axial direction of the driving shaft 20 and both act on the driving shaft 20 to reduce the friction coefficient of the driving shaft 20 and improve the rotational accuracy of the driving shaft 20.

[0050] At Figures 3-5In the specific embodiment shown, the angle between the top wall 111 of the installation cavity and the horizontal plane is 4°-7°. In this way, the angle of the top wall 111 of the installation cavity is made more reasonable, and thus the reasonable inclination angle makes the extension length of the top wall 111 of the installation cavity more reasonable, which can ensure that the lubricating oil driven by the driven gear 50 during forward and reverse rotation can splash onto the top wall 111 of the installation cavity, so as to improve the lubrication stability and always stably lubricate the main shaft bearing 40.

[0051] As Figure 1 , Figure 4 and Figure 5 shown, the minimum distance between the top wall 111 of the installation cavity and the center line of the driven gear 50 is greater than the large end radius of the driven gear 50 by 7 mm - 12 mm. That is to say, the difference between the distance of the area where the inclined top wall 111 of the installation cavity is closest to the center line of the driven gear 50 and the large end radius of the driven gear 50 is 7 mm - 12 mm. In this way, the distance between the top wall 111 of the installation cavity and the driven gear 50 is made more reasonable. While ensuring that the lubricating oil splashed onto the top wall 111 of the installation cavity can be adsorbed on the top wall 111 of the installation cavity, it can further reduce the space occupied by the gearbox 100 and facilitate the layout of the gearbox 100.

[0052] As Figures 2-4 shown, the installation cavity 11 further includes: a bottom wall 112 of the installation cavity, a first side wall 113 of the installation cavity away from the main shaft bearing 40, and a second side wall 114 of the installation cavity close to the main shaft bearing 40. Both ends of the bottom wall are connected to the top wall 111 of the installation cavity through the first side wall 113 and the second side wall 114 of the installation cavity respectively.

[0053] Among them, a certain amount of lubricating oil is accommodated above the bottom wall 112 of the installation cavity. When the driven gear 50 rotates, it can drive the lubricating oil to splash onto the top wall 111 of the installation cavity, the first side wall 113 of the installation cavity, and the second side wall 114 of the installation cavity, and make the inclination angle of the top wall 111 of the installation cavity more reasonable, so as to ensure the extension length of the top wall 111 of the installation cavity, so as to ensure that the lubricating oil attached to the top wall 111 of the installation cavity can fully lubricate the main shaft bearing 40. At the same time, by setting the first side wall 113 and the second side wall 114 of the installation cavity, the lubricating oil that has not splashed into the area where the top wall 111 of the installation cavity is located can quickly return to the area where the bottom wall 112 of the installation cavity is located, improving the oil return speed of the lubricating oil, and further improving the use efficiency of the lubricating oil.

[0054] As Figure 2In the specific embodiment shown, the bottom wall 112 of the installation cavity is configured as an arc surface and the bottom wall 112 of the installation cavity is concentric with the driven gear 50. That is to say, the distance between any position of the bottom wall 112 of the installation cavity and the driven gear 50 is the same. In this way, the amount of lubricating oil splashed by the driven gear 50 during forward rotation is the same as that during reverse rotation, so that the lubrication effects during forward and reverse rotations are the same.

[0055] Optionally, the diameter of the bottom wall 112 of the installation cavity is 10 mm - 15 mm larger than the large end diameter of the driven gear 50. In this way, on the premise of ensuring sufficient lubrication, the space occupied by the box body 10 can be further reduced.

[0056] It should be noted that the box body 10 includes an upper box body 10a and a lower box body 10b. The upper box body 10a and the lower box body 10b jointly define the installation cavity 11. The first installation cavity side wall 113, the installation cavity top wall 111 and the second installation cavity side wall 114 are all formed on the upper box body 10a, and the installation cavity bottom wall 112 is formed on the lower box body 10b. Furthermore, the minimum distance between the installation cavity top wall 111 and the center line of the driven gear 50 is 7 mm - 12 mm larger than the large end radius of the driven gear 50, which can effectively reduce the space occupied by the upper box body 10a, and the diameter of the installation cavity bottom wall 112 is 10 mm - 15 mm larger than the large end diameter of the driven gear 50, which can effectively reduce the space occupied by the lower box body 10b.

[0057] As Figures 3-5 shown, the second installation cavity side wall 114 is configured as an arc surface, the second installation cavity side wall 114 is tangent to the installation cavity bottom wall 112 and the diameter of the second installation cavity side wall 114 is the same as that of the installation cavity bottom wall 112.

[0058] It can be understood that the driven gear 50 is a circular gear. Furthermore, the second installation cavity side wall 114 is configured as an arc surface type, so that the second installation cavity side wall 114 can be closer to the driven gear 50, so that the wall thickness of the area of the box body 10 where the second installation cavity side wall 114 is formed can be set thinner, so as to achieve the purpose of further reducing the space occupied by the box body 10.

[0059] Furthermore, the intersection between the installation cavity top wall 111 and the first installation cavity side wall 113 is rounded with a fillet radius of 35 mm - 45 mm. In this way, the transition between the installation cavity top wall 111 and the first installation cavity side wall 113 is smoother. On the one hand, stress concentration between the installation cavity top wall 111 and the first installation cavity side wall 113 can be avoided, improving the structural strength of the box body 10; on the other hand, lubricating oil accumulation at the intersection between the installation cavity top wall 111 and the first installation cavity side wall 113 can be avoided, improving the use efficiency of the lubricating oil.

[0060] Further, the distance between the end of the top wall 111 of the installation cavity, which is far from the main shaft bearing 40, and the outer wall opposite to the first installation cavity side wall 113 is 8 mm - 12 mm. Thus, the wall thickness of the box body 10 is not less than 8 mm, which can effectively ensure the structural strength of the box body 10.

[0061] According to some embodiments of the present invention, the minimum distance between the first installation cavity side wall 113 and the outer wall opposite thereto is not less than 10 mm. In this way, the thickness of the side wall adjacent to the main shaft 20 is not less than 10 mm, which can further improve the structural strength of the box body 10.

[0062] As Figures 1-8 shown, an oil guide groove 12 is provided on the second installation cavity side wall 114 and is adapted to introduce the lubricating oil on the top wall 111 of the installation cavity into the main shaft bearing 40. In this way, at least part of the lubricating oil adsorbed on the top wall 111 of the installation cavity can be received in the oil guide groove 12, and the lubricating oil can be introduced into the area of the main shaft bearing 40 through the oil guide groove 12, thereby effectively improving the flow efficiency.

[0063] Of course, the installation position of the oil guide groove 12 in the embodiments of the present invention is not limited thereto. In some other embodiments, the oil guide groove is provided on the top wall 111 of the installation cavity and is at least partially adjacent to the main shaft bearing 40 to facilitate the introduction of the lubricating oil into the main shaft bearing 40.

[0064] Further, the included angle between the extending direction of the oil guide groove 12 and the horizontal plane is 10° - 20°. Thus, the flow efficiency of the lubricating oil in the oil guide groove 12 can be further improved.

[0065] It should be noted that the extending direction of the oil guide groove 12 refers to the direction extending from the end connected to the second installation cavity side wall 114 towards the free end. In this embodiment, the oil guide groove 12 extends obliquely upward from the end connected to the second installation cavity side wall 114 towards the first installation cavity side wall 113, with an included angle of 10° - 20°, and the free end at least partially extends into the installation cavity 11 to be adapted to collect the lubricating oil.

[0066] Optionally, an oil guide protrusion 13 is further provided on the second installation cavity side wall 114, and the distance between the free end of the oil guide protrusion 13 and the horizontal plane passing through the center line of the driven gear 50 is 120 mm - 130 mm. Thus, while improving the oil collection efficiency, the length of the oil guide protrusion 13 is made more reasonable, so as to avoid the situation that when the driven gear 50 rotates in reverse, the lubricating oil cannot splash onto the top wall 111 of the installation cavity (the oil guide protrusion 13 is too long), and avoid the situation that when the driving gear 30 rotates forward, the lubricating oil cannot be collected into the oil guide groove 12 (the oil guide protrusion 13 is too short).

[0067] In Figure 6In the specific embodiments shown, the width of the oil guide groove 12 is the same as the width of the installation cavity 11. In this way, it can be ensured that the lubricating oil on the top wall 111 of the installation cavity is fully guided to the area of the main shaft bearing 40, improving the oil guiding effect.

[0068] It should be noted that the width of the installation cavity 11 (refer to Figure 7 ) refers to the distance between the side wall of the box body 10 opposite to one side of the driven gear 50 and the side wall of the box body 10 opposite to the other side of the driven gear 50.

[0069] As Figure 7 shown, a bearing seat 60 is provided between the bearing and the box body 10. An oil collecting groove 61 communicating with the oil guide groove 12 is provided on the bearing seat 60. An oil inlet 62 for guiding the lubricating oil into the main shaft bearing 40 is provided on the bottom wall of the oil collecting groove 61. A first lubricating oil outlet 63 for discharging the lubricating oil is also provided on the bearing seat 60. In this way, the lubricating oil can sequentially pass through the oil guide groove 12, the oil collecting groove 61, the oil inlet 62, the main shaft bearing 40, and the first lubricating oil outlet 63 to return to the bottom wall 112 of the installation cavity, so that the main shaft bearing 40 can obtain sufficient lubrication.

[0070] It should be noted that setting the first lubricating oil outlet 63 can effectively improve the oil return efficiency and oil return speed of the lubricating oil.

[0071] Optionally, a main shaft sleeve 70 is further provided between the main shaft bearing 40 and the main shaft 20. The main shaft sleeve 70 is in interference fit with the main shaft 20. Thus, the main shaft sleeve 70 and the main shaft 20 rotate synchronously, thereby increasing the diameter of the inner ring of the main shaft bearing 40, further improving the bearing capacity of the bearing, reducing the axial vibration of the main shaft 20, and improving the working stability of the gearbox 100. As Figure 8 shown, the gearbox 100 further includes: an end cover 80 and a seal 90. The end cover 80 is provided between the box body 10 and the main shaft 20; the seal 90 is provided inside the end cover 80 and the seal 90 and the end cover 80 are axially abutted in the circumferential direction; wherein the seal 90 and the end cover 80 respectively have a first mating surface 91 and a second mating surface 81 facing each other axially. A plurality of stop protrusions 92 spaced apart in the radial direction are provided on the first mating surface 91, and a plurality of stop grooves 82 spaced apart in the radial direction are provided on the second mating surface 81. Each stop protrusion 92 is in plug-in fit with the corresponding stop groove 82.

[0072] Specifically, as Figure 2 、 Figure 7 and Figure 8As shown, an end cover 80 is also installed on the upper housing 10a of the gearbox 100. The end cover 80 is inserted into the bearing seat 60 and is axially opposite to the seal 90 and circumferentially abuts against it. The seal 90 is sleeved on the driving shaft sleeve 70 and is axially opposite to the first bearing 40a.

[0073] Furthermore, a stop protrusion 92 is formed on the plane (the first mating surface 91) of the seal 90 opposite to the end cover 80, and a stop groove 82 is correspondingly provided on the plane (the second mating surface 81) of the seal opposite to the end cover 80, so as to form a "labyrinth seal" through the stop protrusion 92 inserted into the stop groove 82. In this way, not only can the lubricating oil be prevented from overflowing from the housing 10, but also the connection stability between the end cover 80 and the surrounding components can be improved.

[0074] It should be noted that the seal 90 is sleeved on the driving shaft sleeve 70 and can rotate synchronously with the driving shaft 20.

[0075] Further, the end cover 80 includes a bottom wall portion 83 and a side wall portion 84 provided on the periphery of the bottom wall portion 83 and extending inward. The inner end surface of the bottom wall portion 83 is configured as the second mating surface 81; a circumferential abutting portion 93 is provided on the circumferential surface of the seal 90, and the circumferential abutting portion 93 abuts against the side wall portion 84, and the outer end surface of the seal 90 is configured as the first mating surface 91.

[0076] That is to say, there is a gap between the bottom wall portion 83 of the end cover 80 and the outer end surface of the seal 90, and this gap forms an oil chamber between the end cover 80 and the seal 90 that can accommodate lubricating oil. There is also a gap between the circumferential abutting portion 93 of the seal 90 and the side wall portion 84 of the end cover 80. Thus, the lubricating oil in the housing 10 can enter the "oil chamber" defined by the outer end surface and the bottom wall portion 83 through the gap between the side wall portion 84 and the circumferential abutting portion 93, and then the "labyrinth seal" communicated with this "oil chamber" is used to prevent the lubricating oil from overflowing from the housing 10. A second lubricating oil outlet 841 is also provided on the side wall portion 84, and the lubricating oil in the "oil chamber" can return to the housing 10 through the second lubricating oil outlet 841.

[0077] It can be understood that both the stop protrusion 92 and the stop groove 82 are configured as annular.

[0078] Next, with reference to Figure 4 and Figure 5 the lubrication process of the gearbox 100 according to the embodiments of the present invention will be described in detail.

[0079] Such as Figure 4As shown, the driven gear 50 rotates forward, driving the lubricating oil to splash within the range defined by point P to point Q on the top wall 111 of the installation cavity. The lubricating oil adheres to the top wall 111 of the installation cavity and, under the action of the initial velocity, gravity, and adhesion force of the lubricating oil, flows along the inclined surface of the top wall 111 of the installation cavity towards the oil guiding groove 12. Thus, under the action of the oil guiding groove 12, it flows into the oil collecting groove 61 of the bearing seat 60, and then returns to the oil after flowing through the lubricating oil inlet 62, the first bearing 40a, and the first lubricating oil outlet 63 in sequence, or returns to the oil after flowing through the lubricating oil inlet 62 and the second bearing 40b in sequence, or returns to the oil after flowing through the lubricating oil inlet 62, the second bearing 40b, and the first lubricating oil outlet 63 in sequence.

[0080] As Figure 5 shown, the driven gear 50 rotates in reverse, driving the lubricating oil to splash within the range defined by point P to point Q on the top wall 111 of the installation cavity. The lubricating oil adheres to the top wall 111 of the installation cavity and, under the action of gravity and adhesion force, flows along the inclined surface of the top wall 111 of the installation cavity towards the oil guiding groove 12. Thus, under the action of the oil guiding groove 12, it flows into the oil collecting groove 61 of the bearing seat 60, and then returns to the oil after flowing through the lubricating oil inlet 62, the first bearing 40a, and the first lubricating oil outlet 63 in sequence, or returns to the oil after flowing through the lubricating oil inlet 62 and the second bearing 40b in sequence, or returns to the oil after flowing through the lubricating oil inlet 62, the second bearing 40b, and the first lubricating oil outlet 63 in sequence.

[0081] It should be noted that point P is the adhesion point of the lubricating oil after splashing when the driven gear 50 rotates forward; point M is the adhesion point of the lubricating oil after splashing when the driven gear 50 rotates in reverse. The length limitation of the oil guiding convex portion 13 and the distance limitation between the top wall 111 of the installation cavity and the center line of the driven gear 50 in the above text are both to ensure that the lubricating oil can splash within the range defined by point P and point Q.

[0082] It can be understood that at least part of the lubricating oil adhering to point P will return to the oil under the action of gravity and adhesion force along the rounded transition between the top wall 111 of the installation cavity and the first installation cavity side wall 113.

[0083] In the description of the present invention, it should be understood that the orientation or positional relationship indicated by the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. is based on the orientation or positional relationship shown in the drawings, and is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the present invention.

[0084] In the description of the present invention, the "first feature" and the "second feature" may include one or more of such features.

[0085] In the description of the present invention, the meaning of "a plurality" is two or more.

[0086] In the description of the present invention, that the first feature is "above" or "below" the second feature may include that the first and second features are in direct contact, or may include that the first and second features are not in direct contact but in contact through additional features therebetween.

[0087] In the description of the present invention, that the first feature is "above", "over" and "on" the second feature includes that the first feature is directly above and obliquely above the second feature, or merely means that the horizontal height of the first feature is higher than that of the second feature.

[0088] In the description of this specification, the descriptions with reference to terms such as "one embodiment", "some embodiments", "illustrative embodiments", "examples", "specific examples", or "some examples", etc. mean that the specific features, structures, materials or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic descriptions of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described may be combined in any one or more embodiments or examples in a suitable manner.

[0089] Although the embodiments of the present invention have been shown and described, those of ordinary skill in the art can understand that various changes, modifications, substitutions and variations can be made to these embodiments without departing from the principles and spirit of the present invention, and the scope of the present invention is defined by the claims and their equivalents.

Claims

1. A gearbox for an orbital train, characterized in that, Comprising: A box body, within which an installation cavity for accommodating a driven gear is formed; A driving shaft and a driving gear, the inner end of the driving shaft is provided with the driving gear, the driving shaft obliquely penetrates the box body and the driving gear meshes with the driven gear, and the driving shaft is mounted on the box body through a driving shaft bearing; Wherein The installation cavity includes: a top wall of the installation cavity, the top wall of the installation cavity is configured as an inclined surface that slopes downward towards the driving shaft bearing, so that the lubricating oil splashed onto the top wall of the installation cavity flows towards the driving shaft bearing; The installation cavity further includes: a bottom wall of the installation cavity, a first side wall of the installation cavity far from the driving shaft bearing, and a second side wall of the installation cavity close to the driving shaft bearing, both ends of the bottom wall are connected to the top wall of the installation cavity through the first side wall of the installation cavity and the second side wall of the installation cavity respectively; The bottom wall of the installation cavity is configured as an arc surface and the bottom wall of the installation cavity is concentric with the driven gear; The second side wall of the installation cavity is configured as an arc surface, the second side wall of the installation cavity is tangent to the bottom wall of the installation cavity and the diameter of the second side wall of the installation cavity is the same as the diameter of the bottom wall of the installation cavity.

2. The gearbox for an orbital train according to claim 1, characterized in that, The included angle between the top wall of the installation cavity and the horizontal plane is 4° - 7°.

3. The gearbox for an orbital train according to claim 1, characterized in that, The minimum distance between the top wall of the installation cavity and the center line of the driven gear is greater than the radius of the large end of the driven gear by 7mm - 12mm.

4. The gearbox for an orbital train according to claim 1, characterized in that, The diameter of the bottom wall of the installation cavity is greater than the diameter of the large end of the driven gear by 10mm - 15mm.

5. The gearbox for an orbital train according to claim 1, characterized in that, The intersection between the top wall of the installation cavity and the first side wall of the installation cavity is rounded and the radius of the rounded corner is 35mm - 45mm.

6. The gearbox for an orbital train according to claim 1, characterized in that, The distance between one end of the top wall of the installation cavity far from the driving shaft bearing and the outer side wall opposite to the first side wall of the installation cavity is 8mm - 12mm.

7. The gearbox for an orbital train according to claim 1, characterized in that, The minimum distance between the first side wall of the installation cavity and the outer side wall opposite to it is not less than 10mm.

8. The gearbox for an orbital train according to claim 1, wherein, A oil guiding groove for guiding the lubricating oil on the top wall of the installation cavity to the driving shaft bearing is provided on the second side wall of the installation cavity.

9. The gearbox for an orbital train according to claim 8, characterized in that, The extension direction of the oil guiding groove forms an included angle of 10° - 20° with the horizontal plane.

10. The gearbox for an orbital train according to claim 8, wherein, An oil guiding convex part is further provided on the second side wall of the installation cavity, and the distance between the free end of the oil guiding convex part and the horizontal plane passing through the center line of the driven gear is 120mm - 130mm.

11. The gearbox for an orbital train according to claim 8, characterized in that, The width of the oil guiding groove is the same as the width of the installation cavity.

12. The gearbox for an orbital train according to claim 8, characterized in that, A bearing seat is provided between the bearing and the box body, an oil collecting groove communicated with the oil guiding groove is provided on the bearing seat, and a lubricating oil inlet for guiding the lubricating oil into the driving shaft bearing is provided on the bottom wall of the oil collecting groove.

13. The gearbox for an orbital train according to claim 12, characterized in that, A first lubricating oil outlet for discharging the lubricating oil is further provided on the bearing seat.

14. The gearbox for an orbital train according to any one of claims 1-13, characterized in that, A driving shaft sleeve is further provided between the driving shaft bearing and the driving shaft, and the driving shaft sleeve is in interference fit with the driving shaft.

15. The gearbox for an orbital train according to claim 14, characterized in that, Further comprising: An end cover, the end cover is arranged between the box body and the [missing part]; A sealing member, the sealing member is arranged inside the end cover and the sealing member and the end cover are circumferentially abutted; Wherein The seal and the end cover respectively have a first mating surface and a second mating surface facing each other axially. A plurality of radially spaced-apart stop protrusions are provided on the first mating surface, and a plurality of radially spaced-apart stop grooves are provided on the second mating surface. Each of the stop protrusions is in plug-in fit with the corresponding stop groove.

16. The gearbox for an orbital train according to claim 15, characterized in that, The end cover includes a bottom wall portion and a side wall portion provided on the periphery of the bottom wall portion and extending inwardly. The inner end surface of the bottom wall portion is configured as the second mating surface. A circumferential abutting portion is provided on the circumferential surface of the seal. The circumferential abutting portion abuts against the side wall portion. The outer end surface of the seal is configured as the first mating surface.

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