Planetary gear mechanism, gearbox and working machine

Abstract

The utility model relates to the field of operation machinery, and discloses a planetary gear mechanism, a gearbox and operation machinery. The planet carrier comprises a disc part arranged outside the sun gear shaft in a sleeving mode, a gear supporting shaft vertically connected to the disc part and an oil guide cylinder vertically connected to the disc part, a cylinder cavity of the oil guide cylinder forms a cylinder oil channel used for guiding lubricating oil to flow, and a cylinder notch communicated with the cylinder oil channel and arranged towards the sun gear is formed in the peripheral wall of the oil guide cylinder; and the planetary gear is rotatably arranged outside the gear supporting shaft in a sleeving manner and is meshed with the sun gear. According to the planetary gear mechanism, the lubricating effect on the meshing position of the sun gear and the planetary gear can be effectively improved, so that the lubricating performance of a gearbox is improved, heat produced by the gearbox is reduced, and then the upper limit of the running speed of an operation machine is improved.

Description

Technical Field

[0001] This application belongs to the field of construction machinery technology, specifically relating to a planetary gear mechanism, a gearbox, and construction machinery. Background Technology

[0002] Compared to tracked machinery, wheeled work machines have higher travel speeds and maneuverability. Taking the existing 15-ton wheeled excavator as an example, the maximum travel speed of this type of excavator produced in European countries is 25 km / h, while most domestically produced ones are between 25 km / h and 35 km / h.

[0003] The maximum speed of wheeled work machinery is closely related to the lubrication performance of its transmission. Better transmission lubrication results in a higher maximum speed, and vice versa. Currently, there is still significant room for improvement in the lubrication performance of transmissions, making optimization necessary. Utility Model Content

[0004] The purpose of this application is to provide a planetary gear mechanism, a gearbox, and a working machine that can effectively improve the lubrication effect at the meshing position of the sun gear and planetary gears, thereby improving the lubrication performance of the gearbox.

[0005] To achieve the above objectives, this application provides a planetary gear mechanism, comprising:

[0006] Sun wheel;

[0007] A planetary carrier includes a disk portion fitted around the sun gear shaft, a gear support shaft perpendicularly connected to the disk portion, and an oil guide cylinder perpendicularly connected to the disk portion. The cylinder cavity of the oil guide cylinder is formed as a cylinder oil passage for guiding the flow of lubricating oil. The peripheral wall of the oil guide cylinder has a cylinder notch that communicates with the cylinder oil passage and faces the sun gear.

[0008] A planetary gear is rotatably mounted on the gear support shaft and meshes with the sun gear.

[0009] In some embodiments, multiple planetary gears, gear support shafts, and oil guide cylinders are provided. Multiple gear support shafts are arranged sequentially at intervals along the circumference of the disk portion and multiple planetary gears are fitted on them one-to-one. At least one oil guide cylinder is provided between any two adjacent gear support shafts.

[0010] In some embodiments, the oil guide cylinder is disposed through the disc portion, and a first axial opening and a second axial opening are respectively formed at both axial ends of the oil guide cylinder, and the cylinder notch is formed as a long groove-shaped notch extending from the first axial opening to the second axial opening.

[0011] In some embodiments, the planetary carrier further includes a central cylindrical shaft coaxially connected to the disk portion and sleeved outside the sun gear shaft, and the planetary gear mechanism further includes a second bearing sleeved outside the central cylindrical shaft;

[0012] The first axial opening is located radially outside the second bearing, the second axial opening is located radially outside the sun gear, and the elongated slot notch is oriented towards the sun gear and the second bearing.

[0013] In some embodiments, the oil guide cylinder is an elastic cylindrical pin.

[0014] A second aspect of this application also provides a gearbox, comprising:

[0015] Box shell; and

[0016] The aforementioned planetary gear mechanism is housed within the housing.

[0017] In some embodiments, the housing is provided with an oil reservoir for storing lubricating oil, and the gearbox further includes an oil pump capable of drawing oil from the oil reservoir and supplying oil to the cylinder oil passage.

[0018] In some embodiments, an oil passage is formed in the shell wall of the housing, and the two ends of the oil passage are respectively connected to the oil storage chamber and the oil inlet of the oil pump.

[0019] In some embodiments, the oil pump is disposed inside the housing and driven by the sun gear shaft, and the pump chamber of the oil pump is connected to the housing cavity, so that the internal air pressure of the housing can be kept lower than the external air pressure when the oil pump is in operation.

[0020] A third aspect of this application also provides a working machine that includes the aforementioned gearbox.

[0021] Through the above technical solution, when the gearbox of this application is working, after the lubricating oil enters the oil passage of the guide cylinder, it can flow along the oil passage and then flow to the sun gear through the cylinder notch on the guide cylinder. Since the sun gear rotates and meshes with the planetary gears, the lubricating oil can actively and precisely lubricate the meshing position of the sun gear and planetary gears, improving the lubrication effect at this meshing position and reducing frictional heat generation. In this way, the overall heat generation of the gearbox under high-speed conditions can also be reduced, and the upper speed limit can be increased, thereby increasing the upper speed limit of the working machinery. In addition, since the active lubrication of the meshing position of the sun gear and planetary gears in this application does not require the use of expensive lubricating oil nozzles and other structures, it can effectively control the production and manufacturing costs of the gearbox, and therefore has strong practicality.

[0022] Other features and advantages of the embodiments of this application will be described in detail in the following detailed description section. Attached Figure Description

[0023] The accompanying drawings are provided to further illustrate the embodiments of this application and form part of the specification. They are used together with the following detailed description to explain the embodiments of this application, but do not constitute a limitation on the embodiments of this application. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without any inventive effort. In the drawings:

[0024] Figure 1 This is a structural schematic diagram of a gearbox according to a specific embodiment of this application;

[0025] Figure 2 This is a structural cross-sectional view of a planetary gear mechanism according to a specific embodiment of this application;

[0026] Figure 3 This is an axial schematic diagram of a planetary gear mechanism according to a specific embodiment of this application.

[0027] Explanation of reference numerals in the attached figures

[0028] 10 housing 20 oil pump

[0029] 30 Sun Gear 40 Sun Gear Axle

[0030] 50 Planetary Carrier 60 Planetary Gear

[0031] 70 Gear Ring 80 First Bearing

[0032] 90 Second bearing 100 Third bearing

[0033] 110 Clutch mechanism 120 Braking mechanism

[0034] 130 Transmission gear; 140 Oil baffle structure

[0035] 150 Output flange 160 Control valve block

[0036] 11 Oil reservoir 41 Main oil passage

[0037] 42 First branch oil passage 43 Second branch oil passage

[0038] 44 Third branch oil passage 45 Fourth branch oil passage

[0039] 51 Planetary carrier gear 52 Disc section

[0040] 53 Gear support shaft 54 ​​Center cylinder shaft

[0041] 55 Oil guide cylinder string 56 First planetary carrier oil passage

[0042] 57 Second planetary carrier oil passage 71 Gear ring oil passage

[0043] 111 First disc spring 112 First piston

[0044] 113 First friction plate 114 First steel plate

[0045] 121 Second disc spring 122 Second piston

[0046] 123 Second friction plate 124 Second steel plate

[0047] 141 Oil-separating chamber Detailed Implementation

[0048] The specific embodiments of this application will be described in detail below with reference to the accompanying drawings. It should be understood that the specific embodiments described herein are for illustration and explanation only and are not intended to limit this application.

[0049] Reference Figures 1 to 3 A first exemplary embodiment of this application provides a gearbox, which includes:

[0050] The housing 10 has an oil storage chamber 11 for storing lubricating oil.

[0051] Oil pump 20, the oil inlet of oil pump 20 is connected to oil storage chamber 11;

[0052] A planetary gear mechanism, housed within a housing 10, includes a sun gear shaft 40, a planet carrier 50, and internal bearings. The sun gear shaft 40 contains a shaft oil passage, and the planet carrier 50 contains a planet carrier oil passage communicating with the shaft oil passage.

[0053] The transmission gear 130 is disposed inside the housing 10, and the transmission gear 130 extends partially into the oil storage cavity 11 and meshes with the planet carrier gear 51 of the planet carrier 50.

[0054] The oil pump 20 has its oil outlet, wheel axle oil passage and planetary carrier oil passage connected in sequence. The wheel axle oil passage and / or planetary carrier oil passage can actively lubricate the bearings inside the mechanism. The transmission gear 130 can splash lubricate itself and the planetary carrier gear 51 by agitating the lubricating oil.

[0055] With the above configuration, when the gearbox of this application is working, the oil pump 20 can draw lubricating oil from the oil reservoir 11 and then supply the lubricating oil into the axle oil passage of the sun gear shaft 40 through its own oil outlet. Since the sun gear shaft 40 rotates when the gearbox is working, the lubricating oil in the axle oil passage can flow directly to the internal bearings of the planetary gear mechanism and / or flow to the internal bearings of the mechanism through the planet carrier oil passage under the action of centrifugal force and gravity, thereby achieving active and precise lubrication of the internal bearings of the mechanism, improving the lubrication effect of the internal bearings of the mechanism, and reducing their frictional heat generation. At the same time, the transmission gear 130 can splash lubricate itself and the planet carrier gear 51 by agitating the lubricating oil in the oil reservoir 11.

[0056] Therefore, the gearbox of this application can achieve lubrication through a combination of active lubrication and splash lubrication, which reduces the overall heat generation of the gearbox under high-speed conditions and increases the upper speed limit, thereby increasing the upper speed limit of the working machinery.

[0057] In addition, the active lubrication of the internal bearings in this application does not require the use of expensive lubricating oil nozzles or other structures, which can effectively control the production and manufacturing costs of the gearbox, and therefore has strong practicality.

[0058] In some embodiments, the internal bearing of the mechanism may include a first bearing 80 (e.g., a roller bearing, typically the planetary gear 60 being rotatably connected to the gear support shaft 53 via the first bearing 80) sleeved outside the gear support shaft 53 of the planetary carrier 50. The axle oil passage may include a main oil passage 41 extending axially along the sun gear shaft 40 and a first branch oil passage 42 branching from the main oil passage 41 and penetrating the peripheral wall of the sun gear shaft 40. The planetary carrier oil passage may include a first planetary carrier oil passage 56. A first bearing oil passage is formed in the first bearing 80. Furthermore, the oil outlet of the oil pump 20, the main oil passage 41, the first branch oil passage 42, the first planetary carrier oil passage 56, and the first bearing oil passage are sequentially connected to allow lubricating oil to flow into the first bearing 80.

[0059] With the configuration of this embodiment, when the oil pump 20 is running, the oil pump 20 can take lubricating oil from the oil storage chamber 11 and then supply the lubricating oil into the main oil passage 41 through its own oil outlet. Since the sun gear shaft 40 rotates when the gearbox is working, the lubricating oil in the main oil passage 41 can enter the first branch oil passage 42 under the action of centrifugal force and gravity, and then flow into the first bearing 80 through the first planetary carrier oil passage 56 and the first bearing oil passage, thereby achieving active and precise lubrication of the first bearing 80, improving the lubrication effect of the first bearing 80, and reducing its frictional heat generation.

[0060] In some embodiments, refer to Figure 2The central cylindrical shaft 54 ​​of the planetary carrier 50 is sleeved outside the sun gear shaft 40. The oil inlet of the first planetary carrier oil passage 56 is formed on the inner peripheral wall of the central cylindrical shaft 54 ​​and aligned with the oil outlet of the first branch oil passage 42. The oil outlet of the first planetary carrier oil passage 56 is formed on the outer peripheral wall of the gear support shaft 53 and aligned with the oil inlet of the first bearing oil passage. That is, the first planetary carrier oil passage 56 is formed as an oil passage extending from the central cylindrical shaft 54 ​​of the planetary carrier 50 to the gear support shaft 53. Furthermore, when the first planetary carrier oil passage 56 is in a straight extension form, the length of the first planetary carrier oil passage 56 is shorter, which can shorten the time for lubricating oil to reach the first bearing 80 and is more conducive to ensuring continuous lubrication of the first bearing 80.

[0061] Of course, this embodiment provides only one optional form of the first planetary carrier oil passage 56. In fact, the first planetary carrier oil passage 56 can be set into other different forms according to actual needs, such as a curved and extended form, all of which are within the scope of the concept of this application.

[0062] In some embodiments, the central cylindrical shaft 54 ​​of the planetary carrier 50 is sleeved outside the sun gear shaft 40, and the internal bearing of the mechanism may include a second bearing 90 (e.g., a tapered bearing) sleeved outside the central cylindrical shaft 54. The axle oil passage may include a main oil passage 41 extending axially along the sun gear shaft 40 and a second branch oil passage 43 branching from the main oil passage 41 and penetrating the peripheral wall of the sun gear shaft 40. In this case, the planetary carrier oil passage may include a second planetary carrier oil passage 57 formed on the peripheral wall of the central cylindrical shaft 54, and a second bearing oil passage is formed in the second bearing 90. Furthermore, the oil outlet of the oil pump 20, the main oil passage 41, the second branch oil passage 43, the second planetary carrier oil passage 57, and the second bearing oil passage are sequentially connected to allow lubricating oil to flow into the second bearing 90.

[0063] With the configuration of this embodiment, when the oil pump 20 supplies oil to the main oil passage 41, due to the rotation of the sun gear shaft 40, the lubricating oil in the main oil passage 41 can enter the second branch oil passage 43 under the action of centrifugal force and gravity, and then flow into the second bearing 90 through the second planetary carrier oil passage 57 and the second bearing oil passage, thereby achieving active and precise lubrication of the second bearing 90, improving the lubrication effect of the second bearing 90, and reducing its frictional heat generation. In this way, the overall heat generation of the gearbox under high-speed conditions can be further reduced, the upper speed limit can be further increased, and the upper speed limit of the working machinery can be further increased.

[0064] In some embodiments, the internal bearing of the mechanism may include a third bearing 100 (e.g., a thrust needle roller bearing) sleeved between the central cylinder shaft 54 ​​of the planetary carrier 50 and the sun gear shaft 40. The axle oil passage may include a main oil passage 41 extending axially along the sun gear shaft 40 and a third branch oil passage 44 branching from the main oil passage 41 and penetrating the peripheral wall of the sun gear shaft 40. In this case, a third bearing oil passage is formed in the third bearing 100. Furthermore, the oil outlet of the oil pump 20, the main oil passage 41, the third branch oil passage 44, and the third bearing oil passage are sequentially connected to allow lubricating oil to flow into the third bearing 100.

[0065] As can be seen, with the configuration of this embodiment, when the oil pump 20 supplies oil to the main oil passage 41, due to the rotation of the sun gear shaft 40, the lubricating oil in the main oil passage 41 can also enter the third branch oil passage 44 under the action of centrifugal force and gravity, and then flow into the third bearing 100 through the third bearing oil passage, thereby achieving active and precise lubrication of the third bearing 100, improving the lubrication effect of the third bearing 100, and reducing its frictional heat generation. In this way, the overall heat generation of the gearbox under high-speed conditions can be further reduced, the upper limit of the speed can be further increased, and thus the upper limit of the travel speed of the working machinery can be further increased.

[0066] In some embodiments, the transmission further includes a clutch mechanism 110 connected to the sun gear shaft 40, which is used to switch gears to regulate the transmission speed. The shaft oil passage may include a main oil passage 41 extending axially along the sun gear shaft 40 and a fourth branch oil passage 45 branching from the main oil passage 41 and penetrating the peripheral wall of the sun gear shaft 40. Furthermore, the oil outlet of the oil pump 20, the main oil passage 41, and the fourth branch oil passage 45 are sequentially connected, with the oil outlet of the fourth branch oil passage 45 facing the clutch mechanism 110 to allow lubricating oil to flow into the clutch mechanism 110.

[0067] With the configuration of this embodiment, when the oil pump 20 supplies oil to the main oil passage 41, due to the rotation of the sun gear shaft 40, the lubricating oil in the main oil passage 41 can also enter the fourth branch oil passage 45 under the action of centrifugal force and gravity. The fourth branch oil passage 45 can then discharge the lubricating oil to the clutch mechanism 110, thereby achieving active and precise lubrication of the clutch mechanism 110, improving the lubrication effect of the clutch mechanism 110, and reducing its frictional heat generation. In this way, the overall heat generation of the gearbox under high-speed conditions can be further reduced, and the upper limit of the speed can be further increased, thereby further increasing the upper limit of the travel speed of the working machinery.

[0068] It should be noted that in the sun gear shaft 40, only one of the first branch oil passage 42, the second branch oil passage 43, the third branch oil passage 44 and the fourth branch oil passage 45 can be provided, or at least two of the first branch oil passage 42, the second branch oil passage 43, the third branch oil passage 44 and the fourth branch oil passage 45 can be provided in any combination.

[0069] Furthermore, this application does not limit the number, radius, shape (such as straight extension or curved extension) and other structural parameters of the first branch oil passage 42, the second branch oil passage 43, the third branch oil passage 44 and the fourth branch oil passage 45. For example, the number and radius of each branch oil passage can be designed according to actual needs, so as to reasonably distribute the flow rate of lubricating oil in different branch oil passages.

[0070] In some embodiments, the planetary gear mechanism further includes a gear ring 70 in which a gear ring oil passage 71 is formed. The gearbox also includes a braking mechanism 120 connected to the gear ring 70. The clutch mechanism 110 is located between the oil outlet of the fourth branch oil passage 45 and the oil inlet of the gear ring oil passage 71. The oil outlet of the gear ring oil passage 71 is disposed toward the braking mechanism 120 so that the lubricating oil flowing out of the clutch mechanism 110 can flow into the braking mechanism 120 through the gear ring oil passage 71.

[0071] With the configuration of this embodiment, when the gearbox is working, under the action of centrifugal force and gravity, the lubricating oil flowing out from the clutch mechanism 110 can then flow into the braking mechanism 120 through the gear ring oil passage 71, thereby achieving active and precise lubrication of the braking mechanism 120, improving the lubrication effect of the braking mechanism 120, and reducing its frictional heat generation. In this way, the overall heat generation of the gearbox under high-speed conditions can be further reduced, and the upper limit of the speed can be further increased, thereby further increasing the upper limit of the travel speed of the working machinery.

[0072] As an example, the aforementioned clutch mechanism 110 and braking mechanism 120 can achieve gear shifting adjustment of the transmission through the following structural principle:

[0073] Specifically, refer to Figure 1 The clutch mechanism 110 may include a first disc spring 111, a first piston 112, a first friction plate 113, and a first steel plate 114. The first friction plate 113 is connected to the sun gear shaft 40, and the first steel plate 114 is connected to the gear ring 70. Furthermore, the braking mechanism 120 may include a second disc spring 121, a second piston 122, a second friction plate 123, and a second steel plate 124. The second friction plate 123 is connected to the gear ring 70, and the second steel plate 124 is connected to the housing 10.

[0074] Based on the structure of the clutch mechanism 110 and the braking mechanism 120 described above, the gear shift adjustment of the transmission can be achieved by controlling the clutch mechanism 110 and the braking mechanism 120 through the control valve block 160.

[0075] When switching to first gear is required, the main hydraulic circuit of the machine supplies hydraulic control oil to the control valve block 160. After being depressurized by the control valve block 160, the hydraulic control oil enters the hydraulic circuit of the clutch mechanism 110, pushing the first piston 112 to the left, disengaging the first friction plate 113 and the first steel plate 114. At this time, the hydraulic circuit of the braking mechanism 120 is not supplied with oil, and the second friction plate 123 and the second steel plate 124 are pressed together, connecting the gear ring 70 to the housing 10, and keeping the gear ring 70 stationary. At this time, the planetary gear train participates in the reduction, with a reduction ratio of 1 + Z3 / Z1, where Z1 and Z3 are the number of teeth of the sun gear 30 and the gear ring 70, respectively.

[0076] When switching to second gear is required, the main hydraulic circuit in the machine will supply hydraulic control oil to the control valve block 160. After being depressurized by the control valve block 160, the hydraulic control oil enters the hydraulic circuit of the braking mechanism 120, pushing the second piston 122 to the left, disengaging the second friction plate 123 and the second steel plate 124. At this time, the hydraulic circuit of the clutch mechanism 110 is not supplied with oil, and the first friction plate 113 and the first steel plate 114 are pressed together, connecting the sun gear shaft 40 and the ring gear 70. At this time, the planetary gear train becomes a whole, and the sun gear 30 and the planet carrier 50 rotate at the same speed. The planetary gear train does not participate in deceleration.

[0077] As can be seen, in the embodiments listed above, the planetary gear mechanism serves as a mechanism involved in gear shifting of the transmission. However, since the core concept of this application is the lubrication of the transmission, especially the lubrication of the planetary gear mechanism, the core concept of this application (i.e., the aforementioned various lubrication methods) is also applicable in some transmissions where the planetary gear mechanism does not serve as a mechanism involved in gear shifting. In this case, the planetary gear mechanism can be a local transmission mechanism in the transmission and does not play a role in gear shifting.

[0078] In some embodiments, the planetary carrier 50 may include a disk portion 52 sleeved outside the sun gear shaft 40 and an oil guide cylinder 55 vertically connected to the disk portion 52. The cylinder cavity of the oil guide cylinder 55 is formed as a cylinder oil passage for guiding the flow of lubricating oil, and the peripheral wall of the oil guide cylinder 55 is formed with a cylinder notch that communicates with the cylinder oil passage and faces the sun gear 30.

[0079] It should be noted that this application does not limit how the lubricating oil enters the oil passage of the oil guide cylinder 55. The following will provide a detailed explanation by listing different embodiments, which will not be elaborated here.

[0080] With the configuration of this embodiment, when the gearbox of this application is working, after the lubricating oil enters the oil passage of the oil guide cylinder 55, it can flow along the oil passage and then flow to the sun gear 30 through the cylinder notch on the oil guide cylinder 55. Since the sun gear 30 rotates and meshes with the planetary gear 60, the lubricating oil can actively and accurately lubricate the meshing position of the sun gear 30 and the planetary gear 60, improve the lubrication effect of the meshing position, and reduce its frictional heat generation. In this way, the overall heat generation of the gearbox under high-speed conditions can also be reduced, the upper speed limit can be increased, and thus the upper speed limit of the working machinery can be increased.

[0081] In addition, the active lubrication of the meshing position of the sun gear 30 and the planetary gear 60 in this application can effectively control the production cost of the gearbox because it does not require the use of expensive lubricating oil nozzles and other structures. Therefore, it has strong practicality.

[0082] In some embodiments, refer to Figure 3 Multiple planetary gears 60, gear support shafts 53, and oil guide cylinders 55 are provided. Multiple gear support shafts 53 are arranged sequentially at intervals along the circumference of the disc portion 52, and multiple planetary gears 60 are fitted onto them in a one-to-one correspondence. At least one oil guide cylinder 55 is provided between any two adjacent gear support shafts 53. In this way, a larger amount of lubricating oil can be guided to the meshing position between the sun gear 30 and the planetary gears 60 through multiple oil guide cylinders 55, thereby further enhancing the lubrication effect at this meshing position.

[0083] In some embodiments, the oil guide cylinder 55 can be configured to penetrate the disk portion 52, and a first axial opening and a second axial opening are respectively formed at both axial ends of the oil guide cylinder 55. The cylinder notch is formed as an elongated slot-shaped notch extending from the first axial opening to the second axial opening. In this structure, the oil guide cylinder 55 can theoretically receive oil through the first axial opening, the second axial opening, and the cylinder notch, resulting in a larger oil intake space. This allows for easier access of lubricating oil from the outside and better ensures continuous lubrication of the meshing position of the sun gear 30 and the planetary gear 60.

[0084] In some embodiments, an optional method for lubricating oil to enter the oil passage of the oil guide cylinder 55 is provided. Specifically, the planetary carrier 50 includes a central cylinder 54 coaxially connected to the disk portion 52 and sleeved outside the sun gear shaft 40. The planetary gear mechanism also includes a second bearing 90 sleeved outside the central cylinder 54. The sun gear shaft 40 has a main oil passage 41 extending axially and a second branch oil passage 43 branching from the main oil passage 41 and penetrating the peripheral wall of the sun gear shaft 40. The peripheral wall of the central cylinder 54 has a second planetary carrier oil passage 57, and the second bearing 90 has a second bearing oil passage.

[0085] In addition, the main oil passage 41, the second branch oil passage 43, the second planetary carrier oil passage 57, and the second bearing oil passage are connected in sequence. The first axial opening of the oil guide cylinder 55 is located on the radial outer side of the second bearing 90, and the second axial opening of the oil guide cylinder 55 is located on the radial outer side of the sun gear 30. The long groove-shaped notch of the oil guide cylinder 55 is set towards the sun gear 30 and the second bearing 90.

[0086] With the configuration of this embodiment, when the oil pump 20 supplies oil to the main oil passage 41, due to the rotation of the sun gear shaft 40, the lubricating oil in the main oil passage 41 can enter the second branch oil passage 43 under the action of centrifugal force and gravity, and then flow into the second bearing 90 through the second planetary carrier oil passage 57 and the second bearing oil passage, thereby achieving active and precise lubrication of the second bearing 90. Since the first axial opening of the oil guide cylinder 55 is close to the second bearing 90 and the long groove notch faces the second bearing 90, the lubricating oil thrown out from the second bearing 90 can flow into the cylinder oil passage of the oil guide cylinder 55 through the first axial opening and / or the long groove notch. Then the lubricating oil can flow along the cylinder oil passage to the vicinity of the second axial opening, and through the long groove notch, the lubricating oil is guided to the meshing position of the sun gear 30 and the planetary gear 60, thereby achieving lubrication of the meshing position.

[0087] Of course, since the gearbox can achieve splash lubrication, as long as the oil guide cylinder 55 is placed within the splash lubrication range, splashed lubricating oil can enter the oil passage of the oil guide cylinder 55. In addition, the lubricating oil at the second bearing 90 can also come from splash lubrication, and does not necessarily come from active lubrication.

[0088] In some embodiments, the oil guide column 55 may be made of a flexible cylindrical pin, which is beneficial to greatly reduce costs compared to using a more expensive structure such as a nozzle.

[0089] In some embodiments, the oil pump 20 may be driven by the sun gear shaft 40. The shaft oil passage may include a main oil passage 41 extending axially along the sun gear shaft 40. In this case, the oil inlet of the main oil passage 41 is formed at one end of the sun gear shaft 40 connected to the oil pump 20. This eliminates the need for an oil pipe connecting the oil outlet of the oil pump 20 and the oil inlet of the main oil passage, and eliminates the need for an additional oil pump power source. At the same time, the rotational speed of the oil pump can be matched with that of the sun gear shaft 40, so that the pump oil volume can be adjusted according to the actual rotational speed of the gearbox, thereby reducing energy loss.

[0090] In some embodiments, the oil pump 20 may be a bidirectional internal meshing rotor pump, so that the oil pump 20 can be driven regardless of whether the sun gear shaft 40 rotates forward or backward, thus maintaining the oil pump 20's supply of oil to the main oil passage.

[0091] It should be noted that this application does not limit the driving method of the oil pump 20, that is, the oil pump 20 can also be driven in ways other than using the sun gear shaft 40 mentioned above. For example, the power input shaft of the oil pump 20 can be connected to other rotating parts in the gearbox, or it can be driven by other power sources outside the gearbox (such as other power sources in the working machinery, such as engines or motors).

[0092] In some embodiments, the transmission may also include an overflow valve connected between the oil pump 20 and the oil reservoir 11. When the flow rate of the lubricating oil supplied by the oil pump 20 exceeds a preset maximum value, the overflow valve can be automatically opened to discharge the excess lubricating oil to the oil reservoir 11, thereby reducing the energy consumption of the oil pump 20 and further improving the overall efficiency of the transmission.

[0093] In some embodiments, an oil passage is formed in the wall of the housing 10, with its two ends respectively connected to the oil reservoir 11 and the oil inlet of the oil pump 20. Therefore, the oil inlet of the oil pump 20 does not need to be connected to the oil reservoir 11 via an oil pipe. Furthermore, as can be seen from the foregoing embodiments, the active lubrication method used in the gearbox of this application does not require any oil pipes to be installed inside or outside the housing 10. This simplifies the gearbox structure, reduces manufacturing difficulty, and ensures lubrication without significantly increasing the gearbox's overall dimensions.

[0094] In some embodiments, the oil pump 20 is disposed inside the housing 10, and the pump chamber of the oil pump 20 is connected to the housing cavity of the housing 10. When the oil pump 20 is working, excess gas in the housing cavity of the housing 10 can enter the pump chamber of the oil pump 20, so that the housing cavity of the housing 10 is kept in a slightly negative pressure state. That is, when the oil pump 20 is working, the internal air pressure of the housing 10 can be kept lower than the external air pressure. This can reduce the use of the breather plug in the gearbox, save costs, and improve the overall sealing effect of the gearbox.

[0095] In some embodiments, the gearbox may include an oil baffle structure 140 disposed in an oil reservoir 11. The oil baffle structure 140 has an upwardly opening oil separator 141 and an oil leakage gap connecting the oil separator 141 and the oil reservoir 11, so that the lubricating oil level in the oil separator 141 can be lower than the lubricating oil level in the oil reservoir 11, and the transmission gear 130 partially extends into the oil separator 141 and can reach the lubricating oil in the oil separator 141.

[0096] By setting the oil baffle structure 140, its oil leakage gap can make the lubricating oil level in the oil separator 141 lower than the lubricating oil level in the oil reservoir 11, thereby reducing the contact area between the transmission gear 130 and the lubricating oil in the oil separator 141, effectively reducing the oil churning loss of the transmission gear 130, and thus improving the transmission efficiency of the gearbox.

[0097] It should be noted that the transmission gear 130 can also be used as an output component of the gearbox. For example, a shaft can be set to connect the transmission gear 130 and the output flange 150, and the transmission gear 130 can be used to transmit power to the output flange 150, and then the output flange 150 can be used to transmit power to components outside the gearbox.

[0098] The second exemplary embodiment of this application also provides a planetary gear mechanism, the technical effects of which have been described above and will not be repeated here.

[0099] Specifically, the planetary gear mechanism includes:

[0100] Sun Gear 30;

[0101] The planetary carrier 50 includes a disk portion 52 fitted around the sun gear shaft 40, a gear support shaft 53 perpendicularly connected to the disk portion 52, and an oil guide cylinder 55 perpendicularly connected to the disk portion 52. The cylinder cavity of the oil guide cylinder 55 is formed as a cylinder oil passage for guiding the flow of lubricating oil, and the peripheral wall of the oil guide cylinder 55 has a cylinder notch that communicates with the cylinder oil passage and faces the sun gear 30.

[0102] Planetary gear 60 is rotatably mounted on gear support shaft 53 and meshes with sun gear 30.

[0103] In some embodiments, multiple planetary gears 60, gear support shafts 53, and oil guide cylinders 55 are provided. Multiple gear support shafts 53 are arranged sequentially at intervals along the circumference of the disc portion 52 and multiple planetary gears 60 are fitted on them one by one. At least one oil guide cylinder 55 is provided between any two adjacent gear support shafts 53.

[0104] In some embodiments, the oil guide cylinder 55 is disposed through the disc portion 52, and a first axial opening and a second axial opening are respectively formed at both axial ends of the oil guide cylinder 55, and the cylinder notch is formed as a long groove-shaped notch extending from the first axial opening to the second axial opening.

[0105] In some embodiments, the planet carrier 50 further includes a central cylindrical shaft 54 ​​coaxially connected to the disk portion 52 and sleeved outside the sun gear shaft 40, and the planetary gear mechanism further includes a second bearing 90 sleeved outside the central cylindrical shaft 54;

[0106] The first axial opening is located radially outside the second bearing 90, the second axial opening is located radially outside the sun gear 30, and the elongated groove-shaped notch is set towards the sun gear 30 and the second bearing 90.

[0107] In some embodiments, the oil guide column 55 is an elastic cylindrical pin.

[0108] A third exemplary embodiment of this application also provides a gearbox, comprising:

[0109] Box shell 10; and

[0110] The aforementioned planetary gear mechanism is housed within the housing 10.

[0111] In some embodiments, the housing 10 is provided with an oil reservoir 11 for storing lubricating oil, and the gearbox also includes an oil pump 20 capable of drawing oil from the oil reservoir 11 and supplying oil to the cylinder oil passage.

[0112] In some embodiments, an oil passage is formed in the shell wall of the housing 10, and the two ends of the oil passage are respectively connected to the oil storage chamber 11 and the oil inlet of the oil pump 20.

[0113] In some embodiments, the oil pump 20 is disposed inside the housing 10 and driven by the sun gear shaft 40. The pump chamber of the oil pump 20 is connected to the housing cavity of the housing 10 so that the internal air pressure of the housing 10 can be kept lower than the external air pressure when the oil pump 20 is in operation.

[0114] The fourth exemplary embodiment of this application also provides a working machine, which includes the gearbox in the first or third exemplary embodiment described above. The working machine includes, but is not limited to, engineering machinery such as wheeled excavators.

[0115] In the description of this application, it should be understood that the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this application, "multiple" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0116] In this application, unless otherwise expressly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection, an electrical connection, or a connection that allows communication between components; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise expressly limited. Those skilled in the art can understand the specific meaning of the above terms in this application based on the specific circumstances.

[0117] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of this application. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0118] Although embodiments of this application have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting this application. Those skilled in the art can make changes, modifications, substitutions and variations to the above embodiments within the scope of this application.

Claims

1. A planetary gear mechanism, characterized in that, include: Sun wheel (30); The planetary carrier (50) includes a disk portion (52) sleeved outside the sun gear shaft (40), a gear support shaft (53) vertically connected to the disk portion (52), and an oil guide cylinder (55) vertically connected to the disk portion (52). The cylinder cavity of the oil guide cylinder (55) is formed as a cylinder oil passage for guiding the flow of lubricating oil. The peripheral wall of the oil guide cylinder (55) is formed with a cylinder notch that communicates with the cylinder oil passage and faces the sun gear (30). and The planetary gear (60) is rotatably mounted on the gear support shaft (53) and meshes with the sun gear (30).

2. The planetary gear mechanism according to claim 1, characterized in that, The planetary gears (60), the gear support shafts (53), and the oil guide cylinders (55) are all provided in multiples. The multiple gear support shafts (53) are arranged sequentially at intervals along the circumference of the disc portion (52) and the multiple planetary gears (60) are fitted on them one by one. At least one oil guide cylinder (55) is provided between any two adjacent gear support shafts (53).

3. The planetary gear mechanism according to claim 1, characterized in that, The oil guide cylinder (55) is disposed through the disc portion (52), and the oil guide cylinder (55) has a first axial opening and a second axial opening at its two axial ends, respectively. The cylinder notch is formed as a long groove-shaped notch extending from the first axial opening to the second axial opening.

4. The planetary gear mechanism according to claim 3, characterized in that, The planetary carrier (50) also includes a central cylindrical shaft (54) coaxially connected to the disk portion (52) and sleeved outside the sun gear shaft (40), and the planetary gear mechanism also includes a second bearing (90) sleeved outside the central cylindrical shaft (54); The first axial opening is located radially outside the second bearing (90), the second axial opening is located radially outside the sun gear (30), and the elongated slot notch is oriented toward the sun gear (30) and the second bearing (90).

5. The planetary gear mechanism according to claim 3, characterized in that, The oil guide cylinder (55) is an elastic cylindrical pin.

6. A gearbox, characterized in that, include: Box shell (10); and The planetary gear mechanism according to any one of claims 1 to 5 is disposed within the housing (10).

7. The gearbox according to claim 6, characterized in that, The housing (10) is provided with an oil storage chamber (11) for storing lubricating oil, and the gearbox also includes an oil pump (20) capable of taking oil from the oil storage chamber (11) and supplying oil to the cylinder oil passage.

8. The gearbox according to claim 7, characterized in that, The shell wall of the housing (10) has an oil passage formed in the shell wall, and the two ends of the oil passage are respectively connected to the oil storage chamber (11) and the oil inlet of the oil pump (20).

9. The gearbox according to claim 7, characterized in that, The oil pump (20) is located inside the housing (10) and driven by the sun gear shaft (40). The pump chamber of the oil pump (20) is connected to the housing cavity of the housing (10) so that the internal air pressure of the housing (10) can be kept lower than the external air pressure when the oil pump (20) is working.

10. A working machine, characterized in that, Includes the gearbox according to any one of claims 6 to 9.

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