CN117072627A - Planetary speed change mechanism, electric drive system and automobile - Google Patents

Planetary speed change mechanism, electric drive system and automobile Download PDF

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Publication number
CN117072627A
CN117072627A CN202311012432.XA CN202311012432A CN117072627A CN 117072627 A CN117072627 A CN 117072627A CN 202311012432 A CN202311012432 A CN 202311012432A CN 117072627 A CN117072627 A CN 117072627A
Authority
CN
China
Prior art keywords
gear
ring
planetary
shaft
carrier
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN202311012432.XA
Other languages
Chinese (zh)
Inventor
李伟
赵光瑞
罗廷银
刘星
于闯
于海生
林霄喆
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Wuxi Xingqu Technology Co ltd
Wuxi Xingqu Power Technology Co ltd
Zhejiang Geely Holding Group Co Ltd
Original Assignee
Wuxi Xingqu Technology Co ltd
Wuxi Xingqu Power Technology Co ltd
Zhejiang Geely Holding Group Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Wuxi Xingqu Technology Co ltd, Wuxi Xingqu Power Technology Co ltd, Zhejiang Geely Holding Group Co Ltd filed Critical Wuxi Xingqu Technology Co ltd
Priority to CN202311012432.XA priority Critical patent/CN117072627A/en
Publication of CN117072627A publication Critical patent/CN117072627A/en
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/70—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • H02K7/116—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears

Abstract

The invention provides a planetary speed change mechanism, an electric drive system and an automobile, and relates to the technical field of automobile parts. The planetary speed change mechanism comprises a sun gear, a multi-link planet wheel, a planet carrier, a first annular gear and a second annular gear; the sun gear, the planet carrier, the first annular gear and the second annular gear are coaxially arranged, the multi-link planet gear comprises a large gear and a small gear, the sun gear is arranged on the inner side of the large gear and meshed with the large gear, the second annular gear is arranged on the outer side of the large gear and meshed with the large gear, the first annular gear is at least partially arranged on the outer side of the small gear and meshed with the small gear, and on a variable speed transmission path of the planetary speed change mechanism, the first annular gear is arranged at a low speed transmission end, and the sun gear is arranged at a high speed transmission end. The planetary transmission mechanism of the invention has the advantages of fewer needed components, smaller occupied space and more compact structure on the basis of obtaining a larger transmission ratio, and the multi-link planet wheel has reliable inner and outer side support in the radial direction of the sun wheel, so that the movement stability is high, and the practicability is strong.

Description

Planetary speed change mechanism, electric drive system and automobile
Technical Field
The invention relates to the technical field of automobile parts, in particular to a planetary speed change mechanism, an electric drive system and an automobile.
Background
With the development of new energy automobile industry, automobile electrodynamic technology has become a development trend. In order to meet the use requirement, the electric automobile often needs a battery with larger capacity, and the larger the battery capacity is, the larger the weight of the battery is, which causes the weight of the whole automobile to be increased, and the cruising performance is affected, so the light weight design of the electric automobile becomes the direction of improving the performance of the electric automobile. The electric drive system is an important component of the electric automobile, and under the condition of outputting the same power, the motor rotating speed of the electric drive system is improved, the motor torque is reduced, the weight of the motor can be effectively reduced, and the weight of the electric automobile is reduced. However, a larger gear ratio needs to be achieved by adding more components, occupies a large space, and is disadvantageous for weight reduction.
Disclosure of Invention
The invention aims to solve the problem of how to meet the requirements of large transmission ratio, light weight and compact structure of a transmission system in the related technology to a certain extent.
In order to solve at least one aspect of the above problems at least to some extent, the present invention provides, in a first aspect, a planetary gear mechanism including a sun gear, a multi-planetary gear, a carrier, a first ring gear, and a second ring gear; the sun gear, the planet carrier, the first annular gear and the second annular gear are coaxially arranged, the multi-connected planet gear comprises a large gear and a small gear, the sun gear is arranged on the inner side of the large gear and meshed with the large gear, the second annular gear is arranged on the outer side of the large gear and meshed with the large gear, the first annular gear is at least partially arranged on the outer side of the small gear and meshed with the small gear, and is positioned at a low-speed transmission end and a high-speed transmission end on a variable speed transmission path of the planetary speed change mechanism.
Optionally, at least one of the sun gear shaft of the sun gear and the first ring gear is rotationally connected with the planet carrier.
Optionally, the planet carrier includes a planet axle for mounting the multi-link planet, and the planet carrier further includes at least one of a first carrier body and a second carrier body; the first frame body is rotatably arranged on one side, far away from the pinion, of the large gear around a sun gear shaft of the sun gear along the axial direction of the sun gear, and is connected with the planetary gear shaft; the second frame body is rotatably arranged on one side, far away from the large gear, of the small gear around a sun gear shaft of the sun gear, and the second frame body is connected with the planet gear shaft.
Optionally, the first frame body comprises a first sleeve body coaxial with a sun gear shaft of the sun gear and a first plate body extending along the radial direction of the first sleeve body, and the planetary gear shaft is connected with the first plate body; the inner ring of the first sleeve body is connected with the sun gear shaft through a first bearing, and/or the outer ring of the first sleeve body is connected with a shell for fixing the second annular gear through a second bearing.
Optionally, the second frame body includes a second sleeve body coaxial with the planetary wheel axle and a second plate body extending along the radial direction of the second sleeve body, and the planetary wheel axle is connected with the second plate body; the first annular gear comprises a gear ring body and a gear ring frame connected with the gear ring body, the gear ring body is meshed with the pinion, and the outer ring of the second sleeve body is connected with the gear ring frame through a third bearing;
the radial outer side of the gear ring frame is connected with a shell for fixing the second annular gear through a fourth bearing.
Optionally, the gear ring frame is of a sleeve structure;
the sleeve body structure is provided with a plurality of hole sections with sequentially reduced apertures along the axial direction of the planetary wheel shaft from the large gear to the small gear, wherein the hole section with the largest aperture is a set hole section, the gear ring body is arranged on the inner wall of the set hole section, and the second sleeve body is connected with the hole section with the aperture smaller than that of the set hole section through the third bearing;
and/or, along the direction from the large gear to the small gear in the axial direction of the planetary wheel shaft, the sleeve body structure is formed with a plurality of shaft sections with sequentially reduced outer diameters, wherein the shaft section with the largest outer diameter is a set shaft section, and the gear ring body is arranged on the set shaft section; the fourth bearing is mounted on the shaft section having an outer diameter smaller than an outer diameter of the set shaft section.
Optionally, the outer diameter of the fourth bearing is larger than the outer diameter of the set shaft section;
and/or the fourth bearing is positioned at one end, axially far away from the gear ring body, of the gear ring carrier.
In a second aspect, the present invention provides an electric drive system comprising a planetary transmission as described in the first aspect above.
Optionally, the electric drive system further comprises a motor body, the motor body comprises a stator, a rotor and a shell, the stator, the rotor and the planetary speed change structure are arranged in the shell, a second annular gear of the planetary speed change mechanism is installed on the shell, and the rotor is connected with a sun gear of the planetary speed change mechanism.
In a third aspect, the invention provides an automobile comprising an electric drive system as described in the second aspect above.
Compared with the prior art, in the planetary transmission mechanism, the electric drive system and the automobile, when the planetary transmission mechanism is respectively connected with external parts through the sun gear and the first annular gear, for example, the sun gear is in transmission connection with the rotor of the motor body, when the first annular gear is in transmission connection with a load, the inner side of a large gear of the multi-planetary gear is meshed with the sun gear, the outer side of the large gear is meshed with the second annular gear, the large gear performs planetary motion around the sun gear shaft of the sun gear and rotates around the planet gear shaft of the large gear, the outer side of a small gear of the multi-planetary gear is meshed with the first annular gear, further, the speed reduction and the torque increase are realized, and accordingly the planetary transmission mechanism can obtain a larger speed reduction ratio, that is, through the arrangement of the multi-planetary gear, the first annular gear and the second annular gear, the planetary transmission mechanism can obtain a larger speed reduction ratio.
Drawings
FIG. 1 is a schematic diagram of a planetary gear mechanism in an embodiment of the invention;
FIG. 2 is a schematic diagram of an assembly of a planetary transmission in an embodiment of the invention;
fig. 3 is an assembled schematic view of a planetary gear mechanism in yet another embodiment of the invention.
Reference numerals illustrate:
100-sun gear; 110-sun gear shaft; 200-multiple planet gears; 210-a large gear; 220-pinion gear; 300-planet carrier; 310-a first frame; 311-a first sleeve; 312-a first plate; 320-planetary axles; 330-a second frame; 331-a second sleeve; 332-a second plate; 400-a first annular gear; 410-a gear ring body; 420-ring gear carrier; 421-set the shaft segment; 422-first shaft section; 423-a second shaft section; 424-setting a hole section; 500-a second ring gear; 600-motor body; 610-stator; 620-rotor; 630-a housing; 710—a first bearing; 720-a second bearing; 730-third bearing; 740-fourth bearings; 800-load.
Detailed Description
In order that the above objects, features and advantages of the invention will be readily understood, a more particular description of the invention will be rendered by reference to specific embodiments thereof which are illustrated in the appended drawings.
In the description of the present invention, it should be noted that, unless explicitly specified and limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be either fixedly connected, detachably connected, or integrally connected, for example; can be directly connected or indirectly connected through an intermediate medium. The specific meaning of the above terms in the present invention will be understood in specific cases by those of ordinary skill in the art.
In the description of the present specification, descriptions of the terms "embodiment," "one embodiment," "some embodiments," "illustratively," and "one embodiment" and the like mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or embodiment is included in at least one embodiment or implementation of the present invention. In this specification, schematic representations of the above terms do not necessarily refer to the same examples or implementations. Furthermore, the particular features, structures, materials, or characteristics may be combined in any suitable manner in any one or more embodiments or implementations.
The terms "first," "second," and the like are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. As such, a feature defining "a first" or "a second" may explicitly or implicitly include at least one such feature.
As shown in fig. 1, an embodiment of the present invention provides a planetary transmission mechanism including a sun gear 100, a multi-link planet gear 200, a planet carrier 300, a first ring gear 400, and a second ring gear 500; sun gear 100, carrier 300, first ring gear 400 and second ring gear 500 are coaxially disposed, multi-pinion 200 includes gear wheel 210 and pinion 220, sun gear 100 is on the inside of gear wheel 210 and meshes with gear wheel 210, second ring gear 500 is on the outside of gear wheel 210 and meshes with gear wheel 210, first ring gear 400 is at least partially on the outside of pinion 220 and meshes with pinion 220, first ring gear 400 is on the low-speed drive end and sun gear 100 is on the high-speed drive end on the variable speed drive path of the planetary gear mechanism.
In the present description, the present invention will be described by taking a planetary gear mechanism for deceleration as an example, specifically, the sun gear 100 is connected to a power input, for example, to a rotor 620 of the motor body 600 in a driving manner, and the first ring gear 400 is connected to an external member, for example, to the load 800 as a power output of the planetary gear mechanism. However, it should be appreciated that the planetary transmission mechanism may be used for speed increase without violating the design concept of the present invention and will not be described in detail later.
It should be noted that, in the description of "coaxial" in this specification, for example, the components are not mounted on the same rotating shaft, and those skilled in the art can understand the meaning according to the corresponding context, for example, the sun gear 100, the planet carrier 300, the first ring gear 400, and the second ring gear 500 are coaxially disposed, that is, the axes of the sun gear 100, the planet carrier 300, the first ring gear 400, and the second ring gear 500 coincide, and the large gear 210 and the small gear 220 are coaxially disposed, which will not be described in detail later.
In this way, when the planetary transmission mechanism is respectively connected with external components through the sun gear 100 and the first ring gear 400, for example, the sun gear 100 is in transmission connection with the rotor 620 of the motor body 600, when the first ring gear 400 is in transmission connection with the load 800, the inner side (along the radial inner side of the sun gear 100, similar to the following) of the large gear 210 of the multi-link planetary gear 200 is meshed with the sun gear 100, the outer side is meshed with the second ring gear 500, the large gear 210 performs planetary motion around the sun gear 110 of the sun gear 100 and rotates around the planetary gear 320 thereof, the speed reduction torque increase is realized in the power transmission from the sun gear 100 to the large gear 210, the outer side of the small gear 220 of the multi-link planetary gear 200 is meshed with the first ring gear 400, and further speed reduction torque increase is realized, so that the planetary transmission mechanism can obtain a larger speed reduction ratio, that is, through the arrangement of the multi-link planetary transmission mechanism 200, the first ring gear 400 and the second ring gear 500, in some cases, a plurality of sets of speed reduction units are not required to be arranged to obtain a larger speed reduction ratio, so that the planetary transmission mechanism is required to be meshed with the inner side of the planetary transmission mechanism, and the planetary transmission mechanism has a more compact space, and the inner side, and the planetary transmission mechanism has a more compact size, and high requirements on the inner side, and the space, and the practical transmission mechanism is more flexible, and the space-saving.
The gear ratio from the sun gear to the first ring gear is calculated as follows:
wherein Z is 100 Indicating the number of teeth, Z, of sun gear 100 210 Tooth comb, Z, representing large gear 210 220 Indicating the number of teeth, Z, of pinion 220 400 Representing the number of teeth, Z, of the first ring gear 400 500 Representing the number of teeth, i, of the second ring gear 500 1 The recommended range of (2) is 2.8-13; i.e 2 The recommended range of (2) is 1-50; the recommended range of i is 60 to 500.
As shown in fig. 1, at least one of the sun gear shaft 110 of the sun gear 100 and the first ring gear 400 is optionally rotatably connected with the carrier 300.
Illustratively, the sun gear shaft 110 of the sun gear 100 is rotatably connected with the carrier 300.
Illustratively, the first ring gear 400 is rotatably connected with the carrier 300.
Illustratively, the carrier 300 is rotatably coupled to the sun gear shaft 110 and the carrier 300, respectively.
In this way, the planet carrier 300 can be rotatably supported, when the planet carrier 300 is rotatably connected with the sun gear shaft 110 and the planet carrier 300 respectively, the two axial ends of the planet gear shaft 320 can be reliably rotatably supported, in the working process of the planetary gear shifting mechanism, the offset of the two ends of the planet gear shaft 320 in the radial direction of the sun gear 100 is small, the position stability is high, and the problems of abnormal sound and the like under the high-speed rotation of the multi-link planet gear 200 can be avoided to a certain extent.
As shown in fig. 1, optionally, the planet carrier 300 includes a planet axle 320 for mounting the multi-link planet 200, and the planet carrier 300 further includes at least one of a first carrier body 310 and a second carrier body 330; the first carrier 310 is rotatably disposed around the sun gear shaft 110 of the sun gear 100 along the axial direction of the sun gear 100 on the side of the large gear 210 away from the small gear 220, and the first carrier 310 is connected with the planetary gear shaft 320; the second carrier 330 is rotatably disposed on a side of the pinion 220 away from the bull gear 210 around the sun gear shaft 110 of the sun gear 100, and the second carrier 330 is connected to the planetary gear shaft 320.
It should be appreciated that the large gear 210 and the small gear 220 may be of unitary construction and then mounted on the planetary axle 320, with the multiple planet 200 being connected to the planetary axle 320 by, for example, needle bearings.
Taking the example that the large gear 210 is located on the right side of the small gear 220 and the small gear 220 is located on the left side of the large gear 210 in the axial direction of the planet axle 320 in the drawing, at this time, the first carrier 310 is rotatably disposed on the right side of the large gear 210, the second carrier 330 is rotatably disposed on the left side of the small gear 220, the rotation axes of the first carrier 310 and the second carrier 330 coincide with the axis of the sun axle 110, the planet axle 320 is a cantilever axle when the planet carrier 300 only includes one of the first carrier 310 and the second carrier 330, and the right end of the planet axle 320 is connected with the first carrier 310 when the planet carrier 300 includes the first carrier 310 and the second carrier 330, and the left end of the planet axle 320 is connected with the second carrier 330. In this case, the first carrier 310 and the second carrier 330 may be connected by an intermediate connection structure, for example, an intermediate connection shaft, and the intermediate connection structure may be shifted from the position of the planetary wheel shaft 320 in the circumferential direction of the second ring gear 500, which will not be described in detail herein.
As shown in fig. 1 to 3, in an alternative of the planet carrier 300, the first carrier body 310 includes a first sleeve body 311 coaxial with the sun gear shaft 110 of the sun gear 100 and a first plate body 312 extending radially along the first sleeve body 311, and the planet gear shaft 320 is connected to the first plate body 312;
the inner ring of the first sleeve 311 is connected to the sun gear shaft 110 through a first bearing 710, and/or the outer ring of the first sleeve 311 is connected to a housing 630 for fixing the second ring gear 500 through a second bearing 720.
For example, referring to fig. 2, the outer ring of the first sleeve 311 is formed with a bearing connection portion for connection with the second bearing 720 at a position near the right end, and the inner ring of the first sleeve 311 is formed with a bearing connection portion for connection with the first bearing 710 at a position near the right end.
It should be noted that, the housing 630 may be used not only to mount the second ring gear 500, but also to be a supporting frame of the entire planetary transmission mechanism as a mounting base for each rotational member. The housing 630 may also serve as a mounting frame for the rotor 620 and stator 610 of the motor body 600 of the electric drive system, for example when the planetary gear is used in the electric drive system, in which case the motor housing of the motor body 600, i.e. the housing 630, is preferred.
In this way, the rotational support of the first carrier body 310 can be achieved, and when the inner ring of the first sleeve body 311 is connected with the sun gear shaft 110 through the first bearing 710 and the outer ring of the first sleeve body 311 is connected with the housing 630 for fixing the second ring gear 500 through the second bearing 720, the first sleeve body 311, the first bearing 710 and the second bearing 720 also form the rotational support between the sun gear shaft 110 and the housing 630, not only the rotational support of the sun gear shaft 110, but also the support of the planet carrier 300 at the right end, and the rotational stability of the sun gear shaft 110 and the planet carrier 300 with respect to the housing 630 is high.
As shown in fig. 2, optionally, the second carrier 330 includes a second sleeve 331 coaxial with the planetary gear shaft 320 and a second plate 332 extending radially along the second sleeve 331, where the planetary gear shaft 320 is connected to the second plate 332; the first ring gear 400 includes a ring gear body 410 and a ring gear carrier 420 connected to the ring gear body 410, the ring gear body 410 is engaged with the pinion 220, and an outer ring of the second sleeve 331 is connected to the ring gear carrier 420 through a third bearing 730;
the radially outer side of ring gear carrier 420 is connected to a housing 630 for fixing second ring gear 500 through fourth bearing 740.
It should be noted that, the ring gear body 410 may be integrally connected or detachably connected with the ring gear carrier 420, which is not limited thereto.
In this embodiment, the casing 630 forms a rotary support for the ring gear rack 420 through the fourth bearing 740 on the outer side of the ring gear rack 420, and the second sleeve 331 of the second carrier 330 forms a rotary support with the ring gear rack 420 through the third bearing 730 on the inner side of the ring gear rack 420, so that the floating of the ring gear rack 420 and the second carrier 330 in the radial direction can be reduced to a certain extent, and the movement stability under high-speed operation can be ensured. In addition, when the planet carrier 300 further includes the first carrier body 310 and the inner side of the first carrier body 310 is connected to the first bearing 710 and the outer side is connected to the second bearing 720, the movement stability of the planet carrier 300 and the first ring gear 400 can be further improved. Under such circumstances, the sun gear shaft 110 may be integrally connected or detachably connected with the sun gear 100, and at this time, the left end of the sun gear shaft 110 may not exceed the left end face of the sun gear 100, and the sun gear shaft 110 does not need to be directly connected with the second sleeve 331 or the ring gear frame 420 in a rotating manner, so that the overall weight of the planetary transmission mechanism can be reduced, and the planetary transmission mechanism has a simple structure and strong practicability.
Of course, in other embodiments, the left end of the sun gear shaft 110 may extend at least partially into the second sleeve 331 and be rotatably coupled to the second sleeve 331, and may also be rotatably coupled to the ring gear carrier 420 (not shown in this embodiment).
As shown in fig. 2, alternatively, ring gear carrier 420 is a sleeve structure; along the direction from the large gear 210 to the small gear 220 along the axial direction of the planetary axle 320, the sleeve body structure is formed with a plurality of hole sections with sequentially reduced apertures, wherein the hole section with the largest aperture is a set hole section 424, the gear ring body 410 is arranged on the inner wall of the set hole section 424, and the second sleeve body 331 is connected with the hole section with the aperture smaller than the aperture of the set hole section 424 through a third bearing 730.
Specifically, the sleeve structure is formed with a coaxial stepped hole, the stepped hole includes a plurality of hole segments, for example, the stepped hole is shown to include three hole segments from right to left, the three hole segments are a set hole segment 424, a first hole segment and a second hole segment in sequence, the ring gear body 410 is disposed at the right end of the first hole segment, the third bearing 730 is mounted at the right end of the first hole segment, the first hole segment is used for at least partially accommodating an external component when the first ring gear 400 is connected with the external component, for example, the first hole segment is used for being connected with an input shaft of the load 800, at this time, the input shaft can extend into the first hole segment, the first hole segment and the second hole segment can also extend into an inner hole of the second sleeve 331, but the input shaft and the second hole segment are not connected or rotationally connected. At this time, can improve the compactibility that planetary gear mechanism and external part are connected, reduce its in axial demand space, simple structure, the practicality is strong.
Thus, the second carrier 330 and the ring gear carrier 420 can be rotationally connected, and the second carrier 330 and the ring gear carrier 420 are simple in structure, light in weight and high in practicability.
As shown in fig. 2, alternatively, ring gear carrier 420 is a sleeve structure; the sleeve body structure is formed with a plurality of shaft sections with sequentially reduced outer diameters along the axial direction of the planetary wheel shaft 320 from the large gear 210 to the small gear 220, wherein the shaft section with the largest outer diameter is a set shaft section 421, and the gear ring body 410 is arranged on the set shaft section 421; the fourth bearing 740 is mounted on a shaft section having an outer diameter smaller than the outer diameter of the set shaft section 421.
Illustratively, the three shaft segments are, in order from right to left, a set shaft segment 421, a first shaft segment 422, and a second shaft segment 423, wherein a set bore segment 424 is formed on the set shaft segment 421.
At this time, the connection between the ring gear rack 420, the fourth bearing 740 and the housing 630 is facilitated at the right end, the subsequent connection between the ring gear rack 420 and the external component is facilitated, the weight of the ring gear rack 420 can be reduced to a certain extent, the structure is simple, and the practicability is strong.
As shown in fig. 2, a fourth bearing 740 is located at an end of the ring gear carrier 420 axially remote from the ring gear body 410.
For example, the fourth bearing 740 is mounted on the second shaft segment 423, and at this time, the fourth bearing 740 is axially far from the sun gear 100, so that the rotational support of the ring gear carrier 420 can be better achieved. However, at this time, a structural limitation of the housing 630 may be formed, and the housing 630 may need to be provided in a separate structure, for example, the housing 630 includes a cylinder and an end plate, and the fourth bearing 740 is connected to the end plate, in which case the operation is inconvenient.
Optionally, as shown in fig. 3, the outer diameter of fourth bearing 740 is greater than the outer diameter of set shaft section 421.
For example, the fourth bearing 740 is mounted on the second shaft section 423, and the outer diameter thereof is larger than the outer diameter of the set shaft section 421, so that structural limitation on the housing 630 can be reduced, the housing 630 can include a cylinder, the first ring gear 400 can be inserted into the cylinder through the right end of the cylinder, and the connection with the fourth bearing 740 through the end plate is not required, and the structure is simple.
At this time, when the second ring gear 500 is detachably connected to the housing 630, the outer diameter of the fourth bearing 740 may be larger than the outer diameter of the second ring gear 500, and at this time, the second ring gear 500 may be further placed into the barrel through the right end of the barrel, so that the connection operation of each component is facilitated at the right end of the barrel.
The multiple planetary gears 200 may be provided in a plurality, for example, three multiple planetary gears 200 uniformly distributed in the circumferential direction.
Yet another embodiment of the present invention provides an electric drive system including the planetary transmission mechanism of the above embodiment.
Optionally, the electric drive system further includes a motor body 600, the motor body 600 includes a stator 610, a rotor 620 and a housing 630, the stator 610, the rotor 620 and the planetary transmission structure are disposed in the housing 630, and the second ring gear 500 of the planetary transmission mechanism is mounted on the housing 630.
Optionally, the rotor 620 is connected with the sun gear 100 of the planetary transmission.
Yet another embodiment of the present invention provides an automobile including the planetary transmission mechanism of the above embodiment.
The vehicle and the electric drive system have all the advantageous effects provided by the planetary gear mechanism, which are not described in detail here.
Although the invention is disclosed above, the scope of the invention is not limited thereto. Various changes and modifications may be made by one skilled in the art without departing from the spirit and scope of the invention, and such changes and modifications would fall within the scope of the invention.

Claims (10)

1. A planetary speed change mechanism is characterized by comprising a sun gear (100), a multi-link planet gear (200), a planet carrier (300), a first annular gear (400) and a second annular gear (500); sun gear (100), planet carrier (300), first ring gear (400) and second ring gear (500) coaxial arrangement, multi-link planet wheel (200) include gear wheel (210) and pinion (220), sun gear (100) be in the inboard of gear wheel (210) and with gear wheel (210) mesh, second ring gear (500) are located the outside of gear wheel (210) and with gear wheel (210) mesh, first ring gear (400) are located at least partly in the outside of pinion (220) and with pinion (220) mesh on planetary gear's speed change drive route, first ring gear (400) are located the low-speed transmission end, sun gear (100) are located the high-speed transmission end.
2. The planetary transmission mechanism according to claim 1, characterized in that at least one of a sun gear shaft (110) of the sun gear (100) and the first ring gear (400) is rotatably connected with the carrier (300).
3. The planetary transmission mechanism according to claim 1 or 2, wherein the planet carrier (300) comprises a planet axle (320) for mounting the multi-link planet (200), the planet carrier (300) further comprising at least one of a first carrier body (310) and a second carrier body (330); along the axial direction of the sun gear (100), the first frame body (310) is rotatably arranged on one side, far away from the pinion (220), of the large gear (210) around a sun gear shaft (110) of the sun gear (100), and the first frame body (310) is connected with the planetary gear shaft (320); the second frame body (330) is rotatably arranged on one side, away from the large gear (210), of the pinion (220) around a sun gear shaft (110) of the sun gear (100), and the second frame body (330) is connected with the planetary gear shaft (320).
4. A planetary transmission according to claim 3, characterized in that said first carrier (310) comprises a first sleeve (311) coaxial with the sun gear shaft (110) of said sun gear (100) and a first plate (312) extending radially of said first sleeve (311), said planetary gear shaft (320) being connected to said first plate (312); the inner ring of the first sleeve body (311) is connected with the sun gear shaft (110) through a first bearing (710), and/or the outer ring of the first sleeve body (311) is connected with a shell (630) for fixing the second annular gear (500) through a second bearing (720).
5. A planetary gear set according to claim 3, characterized in that said second carrier (330) comprises a second sleeve (331) coaxial with said planetary axle (320) and a second plate (332) extending radially of said second sleeve (331), said planetary axle (320) being connected to said second plate (332); the first annular gear (400) comprises a gear ring body (410) and a gear ring frame (420) connected with the gear ring body (410), the gear ring body (410) is meshed with the pinion (220), and the outer ring of the second sleeve body (331) is connected with the gear ring frame (420) through a third bearing (730);
the radially outer side of the ring gear carrier (420) is connected to a housing (630) for fixing the second ring gear (500) by a fourth bearing (740).
6. The planetary transmission according to claim 5, characterized in that the ring gear carrier (420) is of a sleeve structure;
the sleeve body structure is provided with a plurality of hole sections with sequentially reduced pore diameters along the axial direction of the planetary wheel shaft (320) from the large gear (210) to the small gear (220), wherein the hole section with the largest pore diameter is a set hole section (424), the gear ring body (410) is arranged on the inner wall of the set hole section (424), and the second sleeve body (331) is connected with the hole section with the pore diameter smaller than that of the set hole section (424) through the third bearing (730);
and/or, along the direction from the large gear (210) to the small gear (220) in the axial direction of the planetary wheel shaft (320), the sleeve body structure is formed with a plurality of shaft sections with sequentially reduced outer diameters, wherein the shaft section with the largest outer diameter is a set shaft section (421), and the gear ring body (410) is arranged on the set shaft section (421); the fourth bearing (740) is mounted on the shaft section having an outer diameter smaller than an outer diameter of the set shaft section (421).
7. The planetary transmission according to claim 6, characterized in that the outer diameter of the fourth bearing (740) is larger than the outer diameter of the set shaft section (421);
and/or the fourth bearing (740) is located at an end of the ring gear carrier (420) axially away from the ring gear body (410).
8. An electric drive system comprising a planetary transmission as claimed in any one of claims 1 to 7.
9. The electric drive system of claim 8, further comprising a motor body (600), the motor body (600) including a stator (610), a rotor (620) and a housing (630), the stator (610), the rotor (620) and the planetary transmission being disposed within the housing (630), the second ring gear (500) of the planetary transmission being mounted on the housing (630), the rotor (620) being connected with the sun gear (100) of the planetary transmission.
10. An automobile comprising an electric drive system according to claim 8 or 9.
CN202311012432.XA 2023-08-10 2023-08-10 Planetary speed change mechanism, electric drive system and automobile Pending CN117072627A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202311012432.XA CN117072627A (en) 2023-08-10 2023-08-10 Planetary speed change mechanism, electric drive system and automobile

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202311012432.XA CN117072627A (en) 2023-08-10 2023-08-10 Planetary speed change mechanism, electric drive system and automobile

Publications (1)

Publication Number Publication Date
CN117072627A true CN117072627A (en) 2023-11-17

Family

ID=88710749

Family Applications (1)

Application Number Title Priority Date Filing Date
CN202311012432.XA Pending CN117072627A (en) 2023-08-10 2023-08-10 Planetary speed change mechanism, electric drive system and automobile

Country Status (1)

Country Link
CN (1) CN117072627A (en)

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