WO2023226266A1 - 齿轮变速装置、传动机构及风力发电机组 - Google Patents

齿轮变速装置、传动机构及风力发电机组 Download PDF

Info

Publication number
WO2023226266A1
WO2023226266A1 PCT/CN2022/122581 CN2022122581W WO2023226266A1 WO 2023226266 A1 WO2023226266 A1 WO 2023226266A1 CN 2022122581 W CN2022122581 W CN 2022122581W WO 2023226266 A1 WO2023226266 A1 WO 2023226266A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
planet
planetary
idler
transmission device
Prior art date
Application number
PCT/CN2022/122581
Other languages
English (en)
French (fr)
Inventor
艾晓岚
杨玉良
高斯
徐洪雷
宋信亮
Original Assignee
北京金风科创风电设备有限公司
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 北京金风科创风电设备有限公司 filed Critical 北京金风科创风电设备有限公司
Publication of WO2023226266A1 publication Critical patent/WO2023226266A1/zh

Links

Images

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
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
    • 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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
    • 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
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • 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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H2057/02039—Gearboxes for particular applications
    • F16H2057/02078—Gearboxes for particular applications for wind turbines
    • 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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H2057/02086—Measures for reducing size of gearbox, e.g. for creating a more compact transmission casing
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/72—Wind turbines with rotation axis in wind direction

Definitions

  • the invention relates to a gear transmission device, which can be used in the transmission mechanism of a wind power generator set to increase the rotation speed of a blade hub to a speed suitable for the operation of the wind power generator set. It can also be widely used in other industrial equipment.
  • the planetary gear system of the traditional wind turbine gear transmission device uses a simple planetary gear system, that is, a planetary gear system composed of four parts: a sun gear, a planet gear bracket, a planet gear, and a ring gear.
  • a simple planetary gear system that is, a planetary gear system composed of four parts: a sun gear, a planet gear bracket, a planet gear, and a ring gear.
  • the present application provides a gear transmission device.
  • the gear transmission device includes a first planetary gear train support sleeve.
  • the first planetary gear train support sleeve includes a first ring gear, a first planet carrier, a first planet gear, and a sun inertia.
  • the planetary idler gear and the planetary idler gear; the planetary idler gear and the first planetary gear are both installed on the first planetary carrier; the first planetary gear includes a pinion gear; the planetary idler gear and the pinion gear are both connected to The first ring gear meshes internally and meshes externally with the sun idler gear; the pinion gear can float radially relative to the first planet carrier; the gear transmission device also has an input shaft, and the input shaft One end is connected to the first ring gear or to the sun idler gear.
  • the planet idler gear cannot float radially relative to the first planet carrier, or the planet idler gear can float radially relative to the first planet carrier and the planet idler gear can float radially relative to the first planet carrier.
  • the maximum radial floating amount of the wheel is not greater than the maximum radial floating amount of the first planet wheel.
  • the first planetary gear train support sleeve further includes a first sun gear; the first planetary gear further includes a large gear and a connecting shaft, and the diameter or number of teeth of the large gear is larger than that of the small gear.
  • the diameter or number of teeth of the gear, the large gear and the small gear are axially offset from each other and axially connected through the connecting shaft; the large gear is externally meshed with the first sun gear.
  • the number of the first planet gears is multiple, wherein the large gears of at least two first planet gears are axially offset from each other and project part of the first planet gears in a plane perpendicular to the axial direction. overlapping.
  • a first bearing is provided between the first planet gear and the first planet carrier, and the first bearing is an aligning bearing.
  • the aligning bearing is used to realize the pinion. floats in the radial direction; and/or,
  • the connecting shaft includes a first shaft section connected to the pinion gear and a second shaft section connected to the large gear.
  • the first shaft section and the second shaft section pass through a coupling shaft that moves in the radial direction. device connection, thereby achieving radial floating of the pinion; and/or
  • the connecting shaft adopts a flexible shaft that deforms along the radial direction, thereby realizing the radial floating of the pinion gear.
  • the first bearing is provided at one end close to the large gear.
  • the first planet carrier includes a base and a base plate located at one end of the base, and the base plate and the base are connected or integrally provided; the base has a base plate, The base plate and the bottom plate are arranged opposite each other and form a first accommodation space for accommodating the large gear. There is a space between the large gear and the base plate and/or the bottom plate. There is the first bearing.
  • the number of the first planet gears is multiple, wherein the large gears of at least two first planet gears are axially offset from each other and project part of the first planet gears in a plane perpendicular to the axial direction. Overlap; and, a partition is provided in the first accommodation space to divide the first accommodation space into two installation spaces distributed along the axial direction, and the large gear with a longer connecting shaft is connected to the connecting The large gears with shorter shafts are respectively located in the two installation spaces.
  • a through hole is provided in the middle of the base plate, and the through hole extends in a direction away from the first accommodation space to form a first barrel portion.
  • the end of the first barrel portion The base plate is provided with a radially extending annular end cover plate.
  • the end cover plate and the base plate are formed in the middle for accommodating the planetary idler gear, the pinion gear, the first ring gear, and the first ring gear. Describe the second accommodation space of the sun idler wheel.
  • the planetary idler gear is sleeved on the planetary idler shaft and a second bearing is provided between the planetary idler gear and the planetary idler shaft.
  • One end of the planetary idler shaft (108) is connected to the planetary idler shaft.
  • the other end of the end cover plate is connected to the base plate, one end of the connecting shaft of the first planetary wheel extends into the second accommodation space, and the pinion gear is sleeved on this end of the connecting shaft. .
  • a middle portion of the input shaft has a second cylindrical portion extending toward the first accommodation chamber, and the second cylindrical portion is inserted into the first cylindrical portion.
  • the base plate is provided with a sleeve structure extending in the direction of the input shaft, one end of the top plate is connected to or integrally arranged with the sleeve structure, and the input shaft Insert the top plate into the first planet carrier to connect with the first ring gear.
  • the number of the planetary idler gears is the same as the number of the first planetary gears, and each of the planetary idler gears and each of the first planetary gears are equally spaced along the circumferential direction of the first ring gear. Arranged alternately.
  • the gear transmission device further includes one or more stages of a second planetary gear train, and the second planetary gear train includes a second ring gear, a second planet carrier, a second planet gear, and a second planet gear train.
  • the second planet gear is installed on the second planet carrier, the second planet gear meshes internally with the second ring gear and meshes externally with the second sun gear; the second planet gear The frame is drivingly connected to the first sun gear or the second sun gear of the previous stage.
  • the second planet carrier includes two mounting plates spaced apart along the axial direction, and an accommodation space for accommodating the second planet gear is formed between the two mounting plates.
  • the second planet wheel is sleeved on the second planet wheel shaft.
  • a third bearing is provided between the second planet wheel and the second planet wheel shaft. Both ends of the second planet wheel shaft are respectively connected to the two mounting devices. plate.
  • the second planet carrier includes a connecting sleeve.
  • One end of the connecting sleeve is integrated with or connected to one of the mounting plates, and the other end is axially close to the first sun gear or front wheel.
  • the direction of the second sun gear of the first stage extends, and the first sun gear or the second sun gear of the previous stage is connected to the connecting sleeve.
  • This application also provides a transmission mechanism, which includes the gear transmission device described in any one of the above.
  • This application also provides a wind power generator set, including a blade hub and a transmission mechanism.
  • the transmission mechanism adopts the transmission mechanism described above.
  • the gear transmission device of the transmission mechanism is connected to the blade hub to connect the The blade hub accelerates to the target speed.
  • the planetary idler gear and pinion gear of the gear transmission device provided by this application can jointly share torque and improve the torque load capacity of the entire first planetary gear train.
  • the torque load of the pinion is reduced, even a smaller-sized pinion can meet the load-bearing requirements. Therefore, more pinions can be arranged under the same volume, so that the small size can be achieved while taking into account the small size.
  • the torque load capacity of the entire first planetary gear train is further improved, so it has a higher torque load density.
  • the gear transmission device by staggering the large gears of at least two first planetary gears in the axial direction and partially overlapping the projections on a plane perpendicular to the axial direction, the gear transmission device can be small in size. and large transmission ratio.
  • the transmission mechanism and wind turbine generator set provided by this application also have the above technical effects because they include the above gear transmission device.
  • Figure 1 is a schematic diagram of a gear transmission provided in an embodiment of the present application.
  • Figure 2 is an axial cross-sectional view of the gear transmission device in Figure 1;
  • Figure 3 is an axial cross-sectional perspective view of the gear transmission device in Figure 1;
  • Figure 4 is a schematic diagram of the first planetary gear train in the gear transmission device of Figure 1, without showing the first planet carrier;
  • Figure 5 is an end schematic diagram of the first planetary gear train in Figure 4, mainly showing the first ring gear, the first planetary gear, the planetary idler gear and the sun idler gear;
  • Figure 6 is a disassembled schematic diagram of the second planetary gear train in Figure 1;
  • Figures 7 and 8 are schematic diagrams of the transmission path of an embodiment of the gear transmission provided by the present application.
  • Figure 7 is a schematic diagram of the transmission path in the A-B direction cross-sectional view in Figure 5.
  • Figure 8 is a schematic diagram of the transmission path in Figure 5. The transmission path from the B-B direction cross-sectional perspective.
  • the gear transmission device includes a first planetary gear train 100 .
  • the first planetary gear train 100 includes a first ring gear 101 , a first planet carrier 102 , a first planetary gear 103 , a sun idler gear 104 and a planetary idler gear 105 .
  • the first planet gear 103 includes a pinion gear 103a installed between the first ring gear 101 and the sun idler gear 104.
  • the pinion gear 103a meshes internally with the first ring gear 101 and externally meshes with the sun idler gear 104 .
  • a planetary idler gear 105 is also mounted between the first ring gear 101 and the sun idler gear 104 .
  • the planet idler gear 105 meshes internally with the first ring gear 101 and meshes externally with the sun idler gear 104 .
  • the planetary idler gear 105 only has direct torque transmission with the first ring gear 101 and the sun idler gear 104 .
  • the sun idler gear 104 has direct torque transmission only with the planet idler gear 105 and the pinion gear 103a.
  • the first planet gear 103 and the planet idler gear 105 are both supported and installed on the first planet carrier 102 .
  • the pinion gear 103a of the first planet gear 103 can float relative to the first planet carrier 102 in the radial direction (the radial direction of the pinion gear 103a) along the revolution direction.
  • the planet idler gear 105 cannot float in the radial direction (the radial direction of the planet idler gear 105) relative to the first planet carrier 102, or although the planet idler gear 105 can float radially in the revolution direction relative to the first planet carrier 102, the maximum diameter
  • the radial floating amount is not greater than the maximum radial floating amount of the first planetary gear 103 .
  • the first planetary gear train 100 in this embodiment also has an input shaft.
  • One end of the input shaft 110 is coaxially connected to the first ring gear 101. Power is input from the input shaft 110 to drive the first ring gear 101 to rotate. Then the first planetary gear 103 and the planetary idler gear 105 are driven to rotate.
  • the sun idler gear 104 and the first ring gear 101 jointly drive the pinion gear 103a of the first planetary gear 103, so that the planetary idler gear 105 and the pinion gear 103a jointly share the torque load of the ring gear. Therefore, the torque load of the pinion gear 103a can be reduced, and the torque load capacity of the entire first planetary gear train 100 can be improved.
  • the first planetary gear train 100 also includes a first sun gear 106 .
  • the first planetary gear 103 also includes a large gear 103b and a connecting shaft 103c.
  • the diameter or the number of teeth of the large gear 103b is larger than the diameter or the number of teeth of the small gear 103a.
  • the large gear 103b and the small gear 103a are axially staggered from each other and realize coaxial transmission connection through the connecting shaft 103c.
  • the large gear 103b of the first planet gear 103 is externally meshed with the first sun gear 106, so that the torque can be further transmitted to the first sun gear 106, and the first sun gear 106 performs torque output. Since the diameter of the large gear 103b is larger than the diameter of the pinion 103a, using the large gear 103b to mesh with the first sun gear 106 for torque output can enable the first planetary gear train 100 to obtain a larger transmission speed ratio.
  • the large gears 103b of at least two first planetary gears 103 are offset from each other along the axial direction and partially overlap in projection in a plane perpendicular to the axial direction.
  • the large gear 103c is axially offset, the distances between the offset large gear 103b and the small gear 103a are unequal in the direction away from the input shaft 110. They are located in Figure 2
  • the large gear 103b on the upper side can be defined as a long-axis gear
  • the large gear 103b on the lower side in Figure 2 can be defined as a short-axis gear.
  • the connecting shafts 103c of the two first planetary gears 103 can be set to different angles.
  • the length is such that the large gears 103b of the two first planetary gears 103 are axially offset from each other.
  • the size of the large gear 103b can be set larger under the same volume condition, thereby helping the first planetary gear train 100 to obtain a larger transmission speed ratio.
  • the first planetary gear train 100 has a higher The torque load capacity, large transmission ratio and small size solve the problem that traditional gear transmission devices cannot take into account the three aspects.
  • a first bearing 107 is provided between the first planet wheel 103 and the first planet carrier 102 so that the first planet wheel 103 can rotate around its own axis relative to the first planet carrier 102 during rotation.
  • one way shown in Figure 2 is that the first bearing 107 adopts a self-aligning bearing, and the self-aligning angle of the self-aligning bearing is used to realize radial floating of the pinion 103a.
  • the maximum radial floating amount is related to the self-aligning angle. Size related.
  • the self-aligning bearing at the end close to the big gear 103b or the end far away from the pinion gear 103a. This can ensure that the pinion gear 103a always remains in contact with the sun idler gear 104 and the first ring gear during the floating process. Good mesh for 101.
  • the hole wall of the gear hole of the large gear 103b extends to both sides in the axial direction to form an extension section.
  • First bearings 107 are provided between the extension sections on both sides and the first planet carrier 102, and two The first bearing 107 is more reliable and stable in bearing.
  • an aligning shaft 103c is used to connect the large gear 103b and the small gear 103.
  • the connecting shaft 103c includes a first shaft section connected to the pinion 103a, a second shaft section connected to the large gear 103b, the first shaft section and The second shaft section is connected by a radially movable coupling.
  • one way to achieve floating is to use a flexible shaft that can deform in the radial direction as the connecting shaft 103c.
  • the number of planetary idler gears 105 and the number of first planetary gears 103 can be set to be the same, and each planetary idler gear 105 and each first planetary gear 103 can be arranged along the first ring gear 101 They are arranged alternately one by one at equal or unequal intervals in the circumferential direction. In this way, the overall force of the first planetary gear train 100 is more balanced, the transmission is smoother, and the service life is longer.
  • the two pinion gears 103a adjacent to the planetary idler gear 104 are respectively connected to the large-diameter gear 103b of the short axis and the large-diameter gear 103b of the long axis, so that the torque transmission is more uniform.
  • the first planet carrier 102 includes a base 1021 and a bottom plate 1022 .
  • the base 1021 has a base plate 1021a and an annular support sleeve 1021c. One end of the support sleeve 1021c is connected to the base plate 1021a, and the other end is connected to the bottom plate 1022.
  • a first accommodation space for accommodating the large gear 103b is formed between the base plate 1021a and the bottom plate 1022.
  • the base plate 1021a and the bottom plate 1022 are both provided with bearing seat holes or bearing seat grooves for installing the first bearing 107.
  • both ends of the large gear 103b of the first planetary gear 103 are respectively supported and connected to the base plate 1021a and the bottom plate 1022 through a first bearing 107.
  • the large gear 103b can be supported only by one first bearing 107, and the first bearings 107 can be both located on the base plate 1021a or the bottom plate 1022; it is also possible that the large gear 103b with a longer connecting shaft 103c can be supported by the first bearing 107.
  • the bearing 107 is supported and connected to the base plate 1022, and the shorter large gear 103b of the connecting shaft 103c can be supported and connected to the base plate 1021a through the first bearing 107, so that the large gears 103b of at least two first planetary gears 103 can be axially connected to each other.
  • the installation requirements are staggered and can meet the installation requirements of the first bearing 107 close to the large gear 103b.
  • a partition can also be provided in the first accommodation space to separate the first accommodation space into two installation spaces in the axial direction.
  • the long gear 103 of the connecting shaft 103c is located in the installation space close to the bottom plate 1022.
  • the connecting shaft 103c is longer.
  • the short large gear 103 is located in the installation space close to the base plate 1021a, which can better support the axially staggered large gear 103b.
  • the long large gear 103b of the connecting shaft 103c can pass through the two first bearings.
  • 107 is supported on the partition plate and the base plate 1022, and the shorter large gear 103b of the connecting shaft 103c is supported on the partition plate and the base plate 1021a through two first bearings 107.
  • a through hole is provided in the middle of the base plate 1021a.
  • the through hole extends in a direction away from the first accommodation space to form a first cylindrical portion 1021b.
  • the end of the first cylindrical portion 1021b is provided with a radial
  • the extended and annular end cover plate 1021d forms a second accommodation space between the end cover plate 1021d and the base plate 1021a for accommodating the planet idler gear 105, the pinion gear 103a, the first ring gear 101, and the sun idler gear 104.
  • the first planet carrier 101 also includes a top plate 1023.
  • the base plate 1021a extends in a direction close to the input shaft 110 to form a sleeve structure 1021e.
  • the sleeve structure 1021e is connected to the top plate 1023.
  • one end of the connecting shaft 103c of the first planetary gear 103 extends into the second accommodation space, and the pinion gear 103a is sleeved on this end of the connecting shaft 103c. This can meet the installation requirements of the planetary idler gear 105 and the pinion gear 103a.
  • the planetary idler gear 105 is sleeved on the planetary idler gear shaft 108 , and a second bearing 109 is provided between the planetary idler gear 105 and the planetary idler gear shaft 108 .
  • One end of the planetary idler shaft 108 is connected to the end cover plate 1021d, and the other end is connected to the base plate 1021a.
  • one end of the input shaft 110 is inserted into the top plate 1023 , and the other end extends axially away from the top plate 1023 for external driving equipment to input torque.
  • One end of the input shaft 110 is inserted into the interior of the first planet carrier 102 .
  • a third bearing 111 is provided between the top plate 1023 of the first planet carrier 102 and the input shaft 110 .
  • One end of the input shaft 110 inserted into the first planet carrier 102 is provided with a connecting disk 1102, which is docked with the first ring gear 101, and an extended second sleeve 1101 is provided in the middle of the end, and the second sleeve 1101 is inserted into the first planet carrier 102.
  • a fourth bearing 112 is provided between the first cylindrical part 1021b and the second cylindrical part 1101.
  • the first planet carrier 102 with the above structure can meet the assembly requirements with the first planet gear 103, the planet idler gear 105, and the first ring gear 101, and is small in size and highly integrated.
  • the structure of the first planet carrier 102 can be flexibly set according to actual needs and is not limited to the above structure, as long as it is a structure that can meet the assembly requirements of the first planet gear 103, the planet idler gear 105, and the first ring gear 101. Can.
  • a balancing torque arm (not shown) may be provided on the outer periphery of the first planet carrier 102 .
  • the torque arm may be an arm structure extending radially from the outer periphery of the first planet carrier 102 .
  • the two torsion arms are symmetrically arranged along the axis.
  • the gear transmission device can also be provided with a second planetary gear train 200.
  • the second planetary gear train 200 includes a second ring gear 201, a second planet carrier 202, a second planet gear 203 and The second sun gear 206.
  • the second planet gear 203 is installed on the second planet carrier 202 .
  • the second planet gear 203 is installed between the second ring gear 201 and the second sun gear 206 .
  • the second planet gear 203 is in internal mesh with the second ring gear 201 and is in external mesh with the second sun gear 206 .
  • only one level of the second planetary gear train 200 can be provided, or a multi-stage (two or more levels) second planetary gear train 200 can be provided.
  • a multi-stage second planetary gear train 200 each level of the second planetary gear train 200
  • the two planetary gear trains 200 are arranged sequentially along the axial direction, and the second planet carrier 202 of the second planetary gear train 200 of the latter stage is drivingly connected to the second sun gear 206 of the second planetary gear train 200 of the previous stage.
  • the second planet carrier 202 includes two mounting plates 202a spaced apart along the axial direction and a connecting arm 202b connecting the two mounting plates 202a.
  • An accommodation space for accommodating the second planet gear 203 is formed between the two mounting plates 202a.
  • the second planet gear 203 is mounted on the second planet gear shaft 204 .
  • a fifth bearing 205 is provided between the second planet gear 203 and the second planet gear shaft 204 .
  • Both ends of the second planetary shaft 204 are respectively connected to the two mounting plates 202a. This can meet the installation requirements of the second planetary gear 203.
  • the second planet carrier 202 may also include a connecting sleeve 202c.
  • One end of the connecting sleeve 202c is connected to a mounting plate 202a. It may also be integrally provided with the mounting plate 202a. The other end is axially close to the first sun gear. 106 or the direction of the second sun gear 206 of the previous stage extends.
  • the connecting sleeve 202c is used to connect the first sun gear 106 or the second sun gear 206 of the previous stage.
  • the second sun gear 206 of the last stage is connected to an output shaft 207, and the output shaft 207 transmits torque to external equipment.
  • the second planet carrier 202 is also provided with a bearing connection part A.
  • Each is provided with a bearing connection A (only one is visible in Figure 7).
  • the second planet carrier 202 is at least partially installed in the bottom plate 1022.
  • the two bearing connection parts A at both ends of the second planet carrier 202 are each equipped with a sixth bearing 210 and a seventh bearing 209. Through the sixth bearing 210 and the seventh bearing 209 Supported by the bottom plate 1022 and the end cover 208 respectively.
  • the second ring gear 201 is connected to the bottom plate 1022 and the end cover 208 on both sides in the axial direction.
  • the first planet carrier 102, the top plate 1023, and the end cover 208 together form the housing of the gear transmission device.
  • the end cover 208 can also be provided with a flange connecting plate 2081, through which the flange connecting plate 2081 can be connected and fixed with external equipment.
  • the second planet carrier 202 with the above structure can meet the assembly requirements with the second planet gear 203, and is small in size and highly integrated.
  • the structure of the second planet carrier 202 can be flexibly set according to actual needs and is not limited to the above structure, as long as it is a structure that can meet the assembly requirements with the second planet gear 203 .
  • the transmission path of the gear transmission in this embodiment is:
  • the input torque acts on the first ring gear 101. Due to the floating design of the first planetary gear 103, it will drive the first idler gear 105 to rotate, driving the sun idler gear 104 to rotate. The sun idler gear 104 and the first ring gear 101 simultaneously drive the first The planet gear 103 rotates, causing the planet idler gear 105 and the pinion gear 103a to revolve with the first planet carrier 102 and also rotate around their own axes. During the torque distribution process, at least part of the torque is transmitted to the planetary idler gear 105 , and then transmitted to the sun idler gear 104 from the planetary idler gear 105 , and then transmitted to the first planetary gear 103 through the sun idler gear 104 and the first ring gear 101 . Pinion 103a. The reliability of the torque input by the first ring gear 101 is high and the meshing load sharing is good.
  • Each pinion gear 103a transmits the torque load to the connected large gear 103b.
  • Each large gear 103b further transmits torque to the first sun gear 106, and each large gear 103b jointly drives the first sun gear 106 and the second planet carrier 202 connected thereto to rotate.
  • the second planet carrier 202 transmits the torque to the second planet gear 203, which transmits the torque to the second sun gear 206 and the output shaft 207 connected thereto, and the output shaft 207 transmits the torque to the external device.
  • the power is input from the first ring gear 101, but it can also be input from the sun idler gear 104.
  • the input torque acts on the sun idler gear 104. Due to the floating design of the first planetary gear 103, it will drive the first idler gear 105 to rotate, and then drive the first ring gear 101 to rotate.
  • the sun idler gear 104 and the first ring gear 101 At the same time, the first planetary gear 103 is driven to rotate, so that the planetary idler gear 105 and the pinion gear 103a revolve with the first planetary carrier 102 and also rotate around their own axes.
  • the core idea of the present application is to make the maximum radial floating amount of the pinion 103a of the first planetary gear 103 not less than (that is, greater than or equal to) the maximum radial floating amount of the planetary idler gear 105 (if it does not float, then The maximum radial floating amount is zero), and the planetary idler gear 105 is used to share the ring gear torque and reduce the load borne by the teeth of the first planetary gear 103. This can take into account the small size and high torque load capacity, and achieve a higher torque load density.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)

Abstract

一种齿轮变速装置，包括第一行星轮系（100），第一行星轮系包括第一齿圈（101）、第一行星架（102）、第一行星轮（103）、太阳惰轮（104）和行星惰轮（105）；行星惰轮和第一行星轮均安装于第一行星架；第一行星轮包括小齿轮（103a）和与小齿轮同轴相连的大齿轮（103b）；行星惰轮和小齿轮均与第一齿圈内啮合并均与太阳惰轮外啮合；小齿轮能相对第一行星架沿径向浮动，还具有输入轴（110），输入轴的一端与第一齿圈连接。该齿轮变速装置具有较高的扭矩载荷密度，能兼顾小体积、大传动速比和高扭矩载荷能力。

Description

齿轮变速装置、传动机构及风力发电机组
本申请要求于2022年05月26日提交中国专利局、申请号为202210583186.2、发明名称为“齿轮变速装置、传动机构及风力发电机组”的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
技术领域
本发明涉及一种齿轮变速装置，可用于风力发电机组的传动机构，用以将叶片轮毂的转速增加至适合风力发电机组运行的转速，也可以广泛运用于其他工业设备。
背景技术
传统的风力发电机组使用齿轮变速装置将主轴中低速但高扭矩的动力转换成有利于发电机发电的高转速低扭矩动力。
传统的风力发电机组的齿轮变速装置的行星轮系采用简单行星轮系，即由太阳轮、行星轮支架、行星轮、齿圈四部分组成的行星轮系。这种行星轮系传动过程中每个轮齿所受的啮合力较大，导致整个行星轮系的扭矩载荷能力受限，不能满足高扭矩载荷能力需求。
增加行星轮的个数能够提升扭矩载荷能力，这又会导致传动速比的减小，不能满足风力发电机组的大传动速比需求。
因此，单纯通过增加行星轮的个数来提升扭矩载荷能力这种方法并不能兼顾小体积、大传动速比需求，因此并不理想。
申请内容
本申请提供一种齿轮变速装置，所述齿轮变速装置包括第一行星轮系支撑套，所述第一行星轮系支撑套包括第一齿圈、第一行星架、第一行星轮、太阳惰轮和行星惰轮；所述行星惰轮和所述第一行星轮均安装于所述第一行星架；所述第一行星轮包括小齿轮；所述行星惰轮和所述小齿轮均 与所述第一齿圈内啮合并均与所述太阳惰轮外啮合；所述小齿轮能相对所述第一行星架沿径向浮动；所述齿轮变速装置还具有输入轴，所述输入轴的一端与所述第一齿圈连接或与太阳惰轮连接。
在一种具体实施方式中，所述行星惰轮不能相对所述第一行星架沿径向浮动，或者，所述行星惰轮能相对所述第一行星架沿径向浮动且所述行星惰轮的最大径向浮动量不大于所述第一行星轮的最大径向浮动量。
在一种具体实施方式中，所述第一行星轮系支撑套还包括第一太阳轮；所述第一行星轮还包括大齿轮和连接轴，所述大齿轮的直径或齿数大于所述小齿轮的直径或齿数，所述大齿轮和所述小齿轮沿轴向相互错开并通过所述连接轴实现轴向连接；所述大齿轮与所述第一太阳轮外啮合。
在一种具体实施方式中，所述第一行星轮的数量为多个，其中，至少两个所述第一行星轮的大齿轮沿轴向相互错开且在垂直于轴向的平面内投影部分重叠。
在一种具体实施方式中，所述第一行星轮和所述第一行星架之间设有第一轴承，所述第一轴承为调心轴承，利用所述调心轴承实现所述小齿轮的沿径向浮动；和/或，
所述连接轴包括与所述小齿轮连接的第一轴段、与所述大齿轮连接的第二轴段，所述第一轴段和所述第二轴段通过沿径向移动的联轴器连接，以此实现所述小齿轮的沿径向浮动；和/或
所述连接轴采用沿径向变形的柔性轴，以此实现所述小齿轮的沿径向浮动。
在一种具体实施方式中，所述第一轴承设置在靠近所述大齿轮的一端。
在一种具体实施方式中，所述第一行星架包括基座和位于所述基座一端的底板，所述底板和所述基座连接或一体设置；所述基座具有基座板，所述基座板和所述底板相对设置并且二者之间形成用于容置所述大齿轮的第一容置空间，所述大齿轮与所述基座板和/或所述底板之间设有所述第一轴承。
在一种具体实施方式中，所述第一行星轮的数量为多个，其中，至少两个所述第一行星轮的大齿轮沿轴向相互错开且在垂直于轴向的平面内投 影部分重叠；且，所述第一容置空间内设有隔板，将所述第一容置空间分隔为沿轴向分布的两个安装空间，所述连接轴较长的大齿轮与所述连接轴较短的大齿轮分别位于两个所述安装空间内。
在一种具体实施方式中，所述基座板的中部设有通孔，所述通孔向远离所述第一容置空间的方向延伸形成第一筒部，所述第一筒部的端部设有径向延伸且呈环形的端盖板，所述端盖板和所述基座板中间形成用于容置所述行星惰轮、所述小齿轮、所述第一齿圈、所述太阳惰轮的第二容置空间。
在一种具体实施方式中，所述行星惰轮套装于行星惰轮轴且所述行星惰轮和所述行星惰轮轴之间设有第二轴承，所述行星惰轮轴(108)一端连于所述端盖板、另一端连于所述基座板，所述第一行星轮的连接轴的一端伸到所述第二容置空间中，所述小齿轮套装于所述连接轴的该端。
在一种具体实施方式中，所述输入轴的中部具有朝向所述第一容置腔室延伸的第二筒部，所述第二筒部插入所述第一筒部中。
在一种具体实施方式中，还包括顶板，所述基座板设有朝向所述输入轴方向延伸的套筒结构，所述顶板一端与所述套筒结构连接或者一体设置，所述输入轴插入所述顶板并进入所述第一行星架内，以与所述第一齿圈连接。
在一种具体实施方式中，所述行星惰轮的数量与所述第一行星轮的数量相同，各个所述行星惰轮和各个所述第一行星轮沿第一齿圈的周向等间隔地交替布置。
在一种具体实施方式中，所述齿轮变速装置还包括一级或多级第二行星轮系，所述第二行星轮系包括第二齿圈、第二行星架、第二行星轮和第二太阳轮，所述第二行星轮安装于所述第二行星架，所述第二行星轮与所述第二齿圈内啮合并与所述第二太阳轮外啮合；所述第二行星架与所述第一太阳轮或者前一级的所述第二太阳轮传动连接。
在一种具体实施方式中，所述第二行星架包括沿轴向间隔设置的两个安装板，两所述安装板之间形成用于容置所述第二行星轮的容置空间，所述第二行星轮套装于第二行星轮轴，所述第二行星轮和所述第二行星轮轴 之间设有第三轴承，所述第二行星轮轴的两端分别连于两个所述安装板。
在一种具体实施方式中，所述第二行星架包括连接套，所述连接套的一端与一所述安装板一体或者相连接，另一端沿轴向向靠近所述第一太阳轮或前一级的所述第二太阳轮的方向延伸，所述第一太阳轮或前一级的所述第二太阳轮连接于所述连接套。
本申请还提供一种传动机构，所述传动机构包括上述任一项所述的齿轮变速装置。
本申请还提供一种风力发电机组，包括叶片轮毂和传动机构，所述传动机构采用上述所述的传动机构，所述传动机构的所述齿轮变速装置与所述叶片轮毂连接，以将所述叶片轮毂增速到目标转速。
本申请提供的齿轮变速装置的行星惰轮和小齿轮能共同分担扭矩，提升整个第一行星轮系的扭矩载荷能力。
而且，由于小齿轮的扭矩载荷得以降低，所以即便采用较小尺寸的小齿轮也能够满足承载需求，因此，在同等体积条件下能够布置更多个小齿轮，从而能在兼顾小体积的情况下通过增多小齿轮的个数来进一步提升整个第一行星轮系的扭矩载荷能力，因此具有较高的扭矩载荷密度。
齿轮变速装置的上述一种实施方式中，通过让至少两个第一行星轮的大齿轮在轴向上错开布置且垂直于轴向的平面上投影部分重叠，能使该齿轮变速装置兼顾小体积和大传动速比。
本申请提供的传动机构和风力发电机组，由于包括上述齿轮变速装置，因此也具有上述技术效果。
附图说明
图1为本申请实施例中提供的齿轮变速装置的示意图；
图2为图1中齿轮变速装置的轴向剖视图；
图3为图1中齿轮变速装置的轴向剖视立体图；
图4为图1齿轮变速装置内第一行星轮系的示意图，未示意出第一行星架；
图5为图4中第一行星轮系的端部示意图，主要示出第一齿圈、第一 行星轮、行星惰轮以及太阳惰轮；
图6为图1中第二行星轮系的拆解示意图；
图7和图8为本申请提供的齿轮变速装置一种实施例的传动路径简示图，图7示意图在图5中A-B向的剖视视角下的传动路径，图8示意出在图5中B-B向的剖视视角下的传动路径。
图1-7中附图标记说明如下：
100-第一行星轮系；
101-第一齿圈；
102-第一行星架；1021-基座，1021a-基座板；1021b-第一筒部；1021c-支撑套；1021d-端盖板；1021e-套筒结构；1022-底板；1023-顶板；A轴承连接部；
103-第一行星轮；103a-小齿轮；103b-大齿轮；103c-连接轴；
104太阳惰轮；105行星惰轮；106第一太阳轮；107-第一轴承；108-行星惰轮轴；109-第二轴承；110-输入轴；111-第二筒部；112-连接盘；
200第二行星轮系；
201第二齿圈；
202第二行星架，202a安装板，202b连接臂，202c连接套；
203第二行星轮；204第二行星轮轴；205第五轴承；
206第二太阳轮；
207输出轴；
208-端盖；2081-法兰接板；
111-第三轴承；112-第四轴承；。
209-第七轴承；210-第六轴承。
具体实施方式
为了使本技术领域的技术人员更好地理解本申请的技术方案，下面结合附图和具体实施方式对本申请的技术方案作进一步的详细说明。
如图1、2所示，该齿轮变速装置包括第一行星轮系100。
第一行星轮系100包括第一齿圈101、第一行星架102、第一行星轮103、太阳惰轮104和行星惰轮105。
第一行星轮103包括小齿轮103a，小齿轮103a安装在第一齿圈101和太阳惰轮104之间。小齿轮103a与第一齿圈101内啮合、与太阳惰轮104外啮合。
行星惰轮105也安装在第一齿圈101和太阳惰轮104之间。行星惰轮105与第一齿圈101内啮合、与太阳惰轮104外啮合。行星惰轮105仅与第一齿圈101和太阳惰轮104有直接扭矩传递。太阳惰轮104仅与行星惰轮105和小齿轮103a有直接扭矩传递。
第一行星轮103和行星惰轮105均支撑安装于第一行星架102。安装好后，第一行星轮103的小齿轮103a能相对第一行星架102沿公转方向有径向(小齿轮103a的径向)浮动。而行星惰轮105不能相对第一行星架102沿径向(行星惰轮105的径向)浮动，或者，行星惰轮105虽然能相对第一行星架102沿公转方向有径向浮动但最大径向浮动量不不大于第一行星轮103的最大径向浮动量。
如图2所示，本实施例中第一行星轮系100还具有输入轴，输入轴110的一端与第一齿圈101同轴连接，动力从输入轴110输入带动第一齿圈101转动，继而驱动第一行星轮103、行星惰轮105转动。
由于采用上述浮动设计，当第一齿圈101在输入扭矩作用下绕轴向旋转时，至少部分扭矩会传递给行星惰轮105，然后由行星惰轮105传递给太阳惰轮104；太阳惰轮104和第一齿圈101共同驱动第一行星轮103的小齿轮103a，使得行星惰轮105和小齿轮103a共同分担齿圈的扭矩载荷。因此能够降低小齿轮103a的扭矩载荷，提升整个第一行星轮系100的扭矩载荷能力。
而且，由于小齿轮103a的扭矩载荷得以降低，所以即便采用较小尺寸的小齿轮103a也能够满足承载需求，因此，在同等体积条件下能够布置更多个小齿轮103a，从而能在兼顾小体积的情况下通过增多小齿轮103a的个数来进一步提升整个第一行星轮系100的扭矩载荷能力，从而能达到较高的扭矩载荷密度。
进一步的，第一行星轮系100还包括第一太阳轮106。第一行星轮103还包括大齿轮103b和连接轴103c。大齿轮103b的直径或齿数大于小齿轮103a的直径或齿数，大齿轮103b和小齿轮103a沿轴向相互错开并通过连接轴103c实现同轴传动连接。
第一行星轮103的大齿轮103b与第一太阳轮106外啮合，从而能将扭矩进一步传递给第一太阳轮106，由第一太阳轮106进行扭矩输出。由于大齿轮103b的直径大于小齿轮103a的直径，所以利用大齿轮103b与第一太阳轮106啮合进行扭矩输出能使第一行星轮系100获得较大的传动速比。
当第一行星轮103的数量为多个(两个或两个以上)时，至少两个第一行星轮103的大齿轮103b沿轴向相互错开且在垂直于轴向的平面内投影部分重叠，如图2所示，在图2的剖视视角下，由于大齿轮103c轴向错开，则沿远离输入轴110的方向，错开的大齿轮103b和小齿轮103a的距离不等，位于图2上侧的大齿轮103b可定义为长轴齿轮，位于图2中下侧的大齿轮103b可定义为短轴齿轮，具体的，可以通过将两个第一行星轮103的连接轴103c设置成不同长度来使这两个第一行星轮103的大齿轮103b沿轴向相互错开。将大齿轮103b沿轴向错开设置，则在同等体积条件下能够将大齿轮103b的尺寸设置得更大一些，从而利于第一行星轮系100获得更大的传动速比。
通过采用上述差异性浮动设计和让至少两个第一行星轮103的大齿轮103b沿轴向相互错开且在垂直于轴向的平面内投影部分重叠，使得第一行星轮系100具有较高的扭矩载荷能力、较大的传动速比和较小的体积，解决了传统齿轮变速装置无法兼顾三者的问题。
具体的，如图2，第一行星轮103和第一行星架102之间设有第一轴承107，以便旋转时第一行星轮103能够相对第一行星架102绕自身轴线自转。
具体的，使第一行星轮103的小齿轮103a能够相对第一行星架102沿径向浮动的方式多种多样。
例如图2所示的一种方式是，上述第一轴承107采用调心轴承，利用调心轴承的调心角实现小齿轮103a的径向浮动，最大径向浮动量的大小与 调心角的大小相关。
这种实施方式下，优选将调心轴承设置在靠近大齿轮103b的一端或者说远离小齿轮103a的一端，这样能够保障小齿轮103a浮动的过程中始终保持与太阳惰轮104和第一齿圈101的良好啮合。
如图2所示，大齿轮103b齿轮孔的孔壁在轴向上向两侧延伸，形成延伸段，两侧的延伸段与第一行星架102之间均设置第一轴承107，设置两个第一轴承107承载更加可靠、稳定，此时采用调心轴103c连接大齿轮103b和小齿轮103。
再例如，实现浮动的一种方式是：将连接轴103c分段设置，连接轴103c包括与小齿轮103a连接的第一轴段、与大齿轮103b连接的第二轴段，第一轴段和第二轴段通过能沿径向移动的联轴器连接。
再例如，实现浮动的一种方式是：连接轴103c采用能沿径向变形的柔性轴。
再例如，还可以采用上述几种方式中的任意两种或两种以上的组合。
具体的，如图4、6，可以将行星惰轮105的数量与第一行星轮103的数量设置得相同，并让各个行星惰轮105和各个第一行星轮103沿第一齿圈101的周向等间隔或不等间隔地一一交替布置。这样，第一行星轮系100的整体受力更均衡，传动更平稳，使用寿命更长。图6中，与行星惰轮104相邻的两个小齿轮103a分别连接短轴的大径齿轮103b和长轴的大径齿轮103b，扭矩传递更为均匀。
具体的，如图2和图3，第一行星架102包括基座1021和底板1022。基座1021具有基座板1021a和环状的支撑套1021c，支撑套1021c的一端连接基座板1021a，另一端连接底板1022。
基座板1021a和底板1022之间形成用于容置大齿轮103b的第一容置空间。基座板1021a和底板1022均设有用于安装第一轴承107的轴承座孔或者轴承座槽。
如图2、3，第一行星轮103的大齿轮103b两端分别通过一个第一轴承107支撑连接于基座板1021a、底板1022。大齿轮103b仅通过一个第一轴承107支撑也可以，一个第一轴承107可以都设于基座板1021a或者都 设于底板1022；也可以是，连接轴103c较长的大齿轮103b通过第一轴承107支撑连接于底板1022，连接轴103c较短的大齿轮103b可通过第一轴承107支撑连接于基座板1021a，这样能满足至少两个第一行星轮103的大齿轮103b沿轴向相互错开的安装要求，且能满足第一轴承107靠近大齿轮103b安装的需求。
第一容置空间中还可以设置隔板，将第一容置空间沿轴向分隔为两个安装空间，连接轴103c较长的大齿轮103位于靠近底板1022的安装空间内，连接轴103c较短的大齿轮103位于靠近基座板1021a的安装空间内，这样可以更好地支撑沿轴向错开的大齿轮103b，此时，连接轴103c较长的大齿轮103b可通过两个第一轴承107支撑于隔板和底板1022，连接轴103c较短的大齿轮103b通过两个第一轴承107支撑于隔板和基座板1021a。
如图2、3所示，基座板1021a的中部设有通孔，通孔向远离第一容置空间的方向延伸形成第一筒部1021b，第一筒部1021b的端部设有径向延伸且呈环形的端盖板1021d，端盖板1021d和基座板1021a中间形成用于容置行星惰轮105、小齿轮103a、第一齿圈101、太阳惰轮104的第二容置空间。第一行星架101还包括顶板1023，基座板1021a沿靠近输入轴110的方向延伸形成套筒结构1021e，套筒结构1021e与顶板1023相连接。
如图2、3，第一行星轮103的连接轴103c的一端伸到第二容置空间中，小齿轮103a套装于连接轴103c的该端。这样能够满足行星惰轮105和小齿轮103a的安装要求。
行星惰轮105套装于行星惰轮轴108，且行星惰轮105和行星惰轮轴108之间设有第二轴承109。行星惰轮轴108一端连于端盖板1021d、另一端连于基座板1021a。
具体的，如图2所示，输入轴110的一端插入顶板1023，另一端沿轴向向远离顶板1023的方向延伸，以外接驱动设备，输入扭矩。输入轴110的一端插入到第一行星架102的内部，此时，第一行星架102的顶板1023和输入轴110之间设有第三轴承111。输入轴110插入第一行星架102内部的一端设有连接盘1102，连接盘1102和第一齿圈101对接，并且该端 的中部还设有延伸的第二套筒1101，第二套筒1101插入到第一行星架102的第一筒部1021b内，这样插装较为可靠，并且为便于转动，还在第一筒部1021b和第二筒部1101之间设置有第四轴承112。
上述结构的第一行星架102能够满足与第一行星轮103、行星惰轮105、第一齿圈101的组装需求，而且体积小，集成度高。当然，第一行星架102的结构可以根据实际需要灵活设置，而不局限于上述结构，只要是能够满足与第一行星轮103、行星惰轮105、第一齿圈101的组装需求的结构即可。
第一行星架102的外周可以设置起平衡作用的扭力臂(图中未示出)，扭力臂可以是自第一行星架102外周径向延伸的臂结构，两个扭力臂沿轴线对称设置。
进一步的，如图2、3所示，该齿轮变速装置还可以设置第二行星轮系200，第二行星轮系200包括第二齿圈201、第二行星架202、第二行星轮203和第二太阳轮206。
第二行星轮203安装于第二行星架202。第二行星轮203安装在第二齿圈201和第二太阳轮206之间。第二行星轮203与第二齿圈201内啮合并与第二太阳轮206外啮合。
具体的，可以仅设置一级第二行星轮系200，也可以设置多级(两级或两级以上)第二行星轮系200，当设置多级第二行星轮系200时，各级第二行星轮系200沿轴向依次布置，后一级第二行星轮系200的第二行星架202与前一级第二行星轮系200的第二太阳轮206传动连接。
具体的，如图7，第二行星架202包括沿轴向间隔设置的两个安装板202a和连接两安装板202a的连接臂202b。两安装板202a之间形成用于容置第二行星轮203的容置空间。
如图3，第二行星轮203套装于第二行星轮轴204。第二行星轮203和第二行星轮轴204之间设有第五轴承205。第二行星轮轴204的两端分别连于两个安装板202a。这样能够满足第二行星轮203的安装需求。
具体的，如图7，第二行星架202还可以包括连接套202c，连接套202c的一端与一安装板202a连接，与安装板202a一体设置也可以，另一端沿轴向靠近第一太阳轮106或前一级的第二太阳轮206的方向延伸。连接套 202c用于连接第一太阳轮106或者前一级的第二太阳轮206。最后一级的第二太阳轮206连有输出轴207，由输出轴207将扭矩传递给外接设备。
具体的，如图7，第二行星架202还设有轴承连接部A，图示实施例中，第二行星架202的连接套202c所在的一端和远离连接套202c的安装板202a所在的一端各设有一个轴承连接部A(图7中仅一个可见)。第二行星架202至少部分安装在底板1022内，第二行星架202两端的两个轴承连接部A各套装有一个第六轴承210、第七轴承209，通过第六轴承210、第七轴承209分别支撑于底板1022和端盖208。第二齿圈201沿轴向的两侧对接于底板1022和端盖208，第一行星架102和顶板1023、端盖208共同组成齿轮变速装置的壳体。
其中，端盖208还可以设置法兰接板2081，通过法兰接板2081实现与外接设备的连接固定。
上述结构的第二行星架202能够满足与第二行星轮203的组装需求，而且体积小，集成度高。当然，第二行星架202的结构可以根据实际需要灵活设置，而不局限于上述结构，只要是能够满足与第二行星轮203的组装需求的结构即可。
如图7和图8，该实施例中的齿轮变速箱的传动路径是：
输入扭矩作用在第一齿圈101上，由于第一行星轮103浮动设计，将驱动第一惰轮105旋转，带动太阳惰轮104旋转，太阳惰轮104和第一齿圈101同时带动第一行星轮103旋转，使行星惰轮105和小齿轮103a随第一行星架102公转的同时还绕自身轴线自转。分配扭矩的过程中，至少部分扭矩传递到行星惰轮105上，再由行星惰轮105传递给太阳惰轮104，再由太阳惰轮104和第一齿圈101传递给第一行星轮103的小齿轮103a。由第一齿圈101输入扭矩的可靠性较高且啮合均载性较好。
每个小齿轮103a将所受扭矩载荷传递给与之相连接的大齿轮103b。各个大齿轮103b进一步将扭矩传递给第一太阳轮106，各个大齿轮103b共同驱动第一太阳轮106以及与之连接的第二行星架202旋转。
第二行星架202将扭矩传递给第二行星轮203，由第二行星轮203传递给第二太阳轮206和与之连接的输出轴207，由输出轴207将扭矩传递 给外接设备。
可以理解，本实施例中动力从第一齿圈101输入，可知从太阳惰轮104输入也可以。此时，输入扭矩作用在太阳惰轮104上，由于第一行星轮103浮动设计，将驱动第一惰轮105旋转，再带动第一齿圈101旋转，太阳惰轮104和第一齿圈101同时带动第一行星轮103旋转，使行星惰轮105和小齿轮103a随第一行星架102公转的同时还绕自身轴线自转。分配扭矩的过程中，至少部分扭矩传递到行星惰轮105上，再由行星惰轮105传递给第一齿圈101，再由太阳惰轮104和第一齿圈101传递给第一行星轮103的小齿轮103a。
综上，本申请的核心思想是通过让第一行星轮103的小齿轮103a的最大径向浮动量不小于(即大于或等于)行星惰轮105的最大径向浮动量(如果不浮动，则最大径向浮动量为零)，利用行星惰轮105分担齿圈扭矩，降低第一行星轮103轮齿承担的载荷，这样能兼顾小体积和高扭矩载荷能力，达到较高的扭矩载荷密度。另外，通过让至少两个第一行星轮103的大齿轮103b在轴向上错开布置且垂直于轴向的平面上投影部分重叠，来兼顾小体积和大传动速比。
以上应用了具体个例对本申请的原理及实施方式进行了阐述，以上实施例的说明只是用于帮助理解本申请的方法及其核心思想。应当指出，对于本技术领域的普通技术人员来说，在不脱离本申请原理的前提下，还可以对本申请进行若干改进和修饰，这些改进和修饰也落入本申请权利要求的保护范围内。

Claims (18)

  1. 一种齿轮变速装置，其特征在于，所述齿轮变速装置包括第一行星轮系(100)，所述第一行星轮系(100)包括第一齿圈(101)、第一行星架(102)、第一行星轮(103)、太阳惰轮(104)和行星惰轮(105)；所述行星惰轮(105)和所述第一行星轮(103)均安装于所述第一行星架(102)；所述第一行星轮(103)包括小齿轮(103a)；所述行星惰轮(105)和所述小齿轮(103a)均与所述第一齿圈(101)内啮合并均与所述太阳惰轮(104)外啮合；所述小齿轮(103a)能相对所述第一行星架(102)沿径向浮动；所述齿轮变速装置还具有输入轴(110)，所述输入轴(110)的一端与所述第一齿圈(101)连接或与太阳惰轮(104)连接。
  2. 根据权利要求1所述的齿轮变速装置，其特征在于，所述行星惰轮(105)不能相对所述第一行星架(102)沿径向浮动，或者，所述行星惰轮(105)能相对所述第一行星架(102)沿自身径向浮动且所述行星惰轮(105)的最大径向浮动量不大于所述第一行星轮(103)的最大径向浮动量。
  3. 根据权利要求2所述的齿轮变速装置，其特征在于，所述第一行星轮系(100)还包括第一太阳轮(106)；所述第一行星轮(103)还包括大齿轮(103b)和连接轴(103c)，所述大齿轮(103b)的直径或齿数大于所述小齿轮(103a)的直径或齿数，所述大齿轮(103b)和所述小齿轮(103a)沿轴向相互错开并通过所述连接轴(103c)实现轴向连接；所述大齿轮(103b)与所述第一太阳轮(106)外啮合。
  4. 根据权利要求3所述的齿轮变速装置，其特征在于，所述第一行星轮(103)的数量为多个，其中，至少两个所述第一行星轮(103)的大齿轮(103b)沿轴向相互错开且在垂直于轴向的平面内投影部分重叠。
  5. 根据权利要求3所述的齿轮变速装置，其特征在于，所述第一行星轮(103)和所述第一行星架(102)之间设有第一轴承(107)，所述第一轴承(107)为调心轴承，利用所述调心轴承实现所述小齿轮(103a)的沿径向浮动；和/或，
    所述连接轴(103c)包括与所述小齿轮(103a)连接的第一轴段、与所述大齿轮(103b)连接的第二轴段，所述第一轴段和所述第二轴段通过沿径向移动的联轴器连接，以此实现所述小齿轮(103a)的沿径向浮动；和/或
    所述连接轴(103c)采用沿径向变形的柔性轴，以此实现所述小齿轮(103a)的沿径向浮动。
  6. 根据权利要求5所述的齿轮变速装置，其特征在于，所述第一轴承(107)设置在靠近所述大齿轮(103b)的一端。
  7. 根据权利要求3-6任一项所述的齿轮变速装置，其特征在于，所述第一行星架(102)包括基座(1021)和位于所述基座(1021)一端的底板(1022)，所述底板(1022)和所述基座(1021)连接或一体设置；所述基座(1021)具有基座板(1021a)，所述基座板(1021a)和所述底板(1022)相对设置并且二者之间形成用于容置所述大齿轮(103b)的第一容置空间，所述大齿轮(103b)与所述基座板(1021a)和/或所述底板(1022)之间设有所述第一轴承(107)。
  8. 根据权利要求7所述的齿轮变速装置，其特征在于，所述第一行星轮(103)的数量为多个，其中，至少两个所述第一行星轮(103)的大齿轮(103b)沿轴向相互错开且在垂直于轴向的平面内投影部分重叠；且，所述第一容置空间内设有隔板，将所述第一容置空间分隔为沿轴向分布的两个安装空间，所述连接轴(103c)较长的大齿轮(103a)与所述连接轴(103c)较短的大齿轮(103b)分别位于两个所述安装空间内。
  9. 根据权利要求7所述的齿轮变速装置，其特征在于，所述基座板(1021a)的中部设有通孔，所述通孔向远离所述第一容置空间的方向延伸形成第一筒部(1021b)，所述第一筒部(1021b)的端部设有径向延伸且呈环形的端盖板(1021d)，所述端盖板(1021d)和所述基座板(1021a)中间形成用于容置所述行星惰轮(105)、所述小齿轮(103a)、所述第一齿圈(101)、所述太阳惰轮(104)的第二容置空间。
  10. 根据权利要求9所述的齿轮变速装置，其特征在于，所述行星惰轮(105)套装于行星惰轮轴(108)且所述行星惰轮(105)和所述行星惰 轮轴(108)之间设有第二轴承(109)，所述行星惰轮轴(108)一端连于所述端盖板(1021d)、另一端连于所述基座板(1021a)，所述第一行星轮(103)的连接轴(103c)的一端伸到所述第二容置空间中，所述小齿轮(103a)套装于所述连接轴(103c)的该端。
  11. 根据权利要求9所述的齿轮变速装置，其特征在于，所述输入轴(1023b)的中部具有朝向所述第一容置腔室延伸的第二筒部(111)，所述第二筒部(111)插入所述第一筒部(1021b)中。
  12. 根据权利要求11所述的齿轮变速装置，其特征在于，还包括顶板(1023)，所述基座板(1021a)设有朝向所述输入轴(110)方向延伸的套筒结构(1021e)，所述顶板(1023)一端与所述套筒结构(1021e)连接或者一体设置，所述输入轴(110)插入所述顶板(1023)并进入所述第一行星架(102)内，以与所述第一齿圈(101)连接。
  13. 根据权利要求1-6任一项所述的齿轮变速装置，其特征在于，所述行星惰轮(105)的数量与所述第一行星轮(103)的数量相同，各个所述行星惰轮(105)和各个所述第一行星轮(103)沿第一齿圈(101)的周向交替布置。
  14. 根据权利要求1-6任一项所述的齿轮变速装置，其特征在于，所述齿轮变速装置还包括一级或多级第二行星轮系(200)，所述第二行星轮系(200)包括第二齿圈(201)、第二行星架(202)、第二行星轮(203)和第二太阳轮(206)，所述第二行星轮(203)安装于所述第二行星架(202)，所述第二行星轮(203)与所述第二齿圈(201)内啮合并与所述第二太阳轮(206)外啮合；所述第二行星架(202)与所述第一太阳轮(106)或者前一级的所述第二太阳轮(206)传动连接。
  15. 根据权利要求14所述的齿轮变速装置，其特征在于，所述第二行星架(202)包括沿轴向间隔设置的两个安装板(202a)，两所述安装板(202a)之间形成用于容置所述第二行星轮(203)的容置空间，所述第二行星轮(203)套装于第二行星轮轴(204)，所述第二行星轮(203)和所述第二行星轮轴(204)之间设有第三轴承(205)，所述第二行星轮轴(204)的两端分别连于两个所述安装板(202a)。
  16. 根据权利要求15所述的齿轮变速装置，其特征在于，所述第二行星架(202)包括连接套(202c)，所述连接套(202c)的一端与一所述安装板(202a)一体或者相连接，另一端沿轴向向靠近所述第一太阳轮(106)或前一级的所述第二太阳轮(206)的方向延伸，所述第一太阳轮(106)或前一级的所述第二太阳轮(206)连接于所述连接套(202c)。
  17. 传动机构，其特征在于，所述传动机构包括权利要求1-16任一项所述的齿轮变速装置。
  18. 风力发电机组，包括叶片轮毂和传动机构，其特征在于，所述传动机构采用权利要求17所述的传动机构，所述传动机构的所述齿轮变速装置与所述叶片轮毂连接，以将所述叶片轮毂增速到目标转速
PCT/CN2022/122581 2022-05-26 2022-09-29 齿轮变速装置、传动机构及风力发电机组 WO2023226266A1 (zh)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN202210583186.2A CN114922941A (zh) 2022-05-26 2022-05-26 齿轮变速装置、传动机构及风力发电机组
CN202210583186.2 2022-05-26

Publications (1)

Publication Number Publication Date
WO2023226266A1 true WO2023226266A1 (zh) 2023-11-30

Family

ID=82810438

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2022/122581 WO2023226266A1 (zh) 2022-05-26 2022-09-29 齿轮变速装置、传动机构及风力发电机组

Country Status (2)

Country Link
CN (1) CN114922941A (zh)
WO (1) WO2023226266A1 (zh)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114922941A (zh) * 2022-05-26 2022-08-19 北京金风科创风电设备有限公司 齿轮变速装置、传动机构及风力发电机组

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101338812A (zh) * 2008-07-14 2009-01-07 江苏泰隆减速机股份有限公司 水力发电变速装置
JP2010196772A (ja) * 2009-02-25 2010-09-09 Mitsubishi Heavy Ind Ltd 多段式遊星歯車変速装置
CN102753858A (zh) * 2010-02-12 2012-10-24 蒂姆肯公司 具有提高的承载能力的行星齿轮传动系
CN110094464A (zh) * 2019-04-29 2019-08-06 华东交通大学 一种风电齿轮箱
CN110939694A (zh) * 2019-12-27 2020-03-31 郭爱贵 一种适用于非均布多行星轮系的均载装置
CN114645925A (zh) * 2022-03-15 2022-06-21 新疆金风科技股份有限公司 齿轮变速装置、传动机构及风力发电机组
CN114922941A (zh) * 2022-05-26 2022-08-19 北京金风科创风电设备有限公司 齿轮变速装置、传动机构及风力发电机组

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101338812A (zh) * 2008-07-14 2009-01-07 江苏泰隆减速机股份有限公司 水力发电变速装置
JP2010196772A (ja) * 2009-02-25 2010-09-09 Mitsubishi Heavy Ind Ltd 多段式遊星歯車変速装置
CN102753858A (zh) * 2010-02-12 2012-10-24 蒂姆肯公司 具有提高的承载能力的行星齿轮传动系
CN110094464A (zh) * 2019-04-29 2019-08-06 华东交通大学 一种风电齿轮箱
CN110939694A (zh) * 2019-12-27 2020-03-31 郭爱贵 一种适用于非均布多行星轮系的均载装置
CN114645925A (zh) * 2022-03-15 2022-06-21 新疆金风科技股份有限公司 齿轮变速装置、传动机构及风力发电机组
CN114922941A (zh) * 2022-05-26 2022-08-19 北京金风科创风电设备有限公司 齿轮变速装置、传动机构及风力发电机组

Also Published As

Publication number Publication date
CN114922941A (zh) 2022-08-19

Similar Documents

Publication Publication Date Title
WO2023173623A1 (zh) 齿轮变速装置、传动机构及风力发电机组
EP2184488A1 (en) Split torque compound planetary drivetrain for wind turbine applications
US11078989B2 (en) Reduction gear and electromechanical device
WO2023226266A1 (zh) 齿轮变速装置、传动机构及风力发电机组
CN110094464B (zh) 一种风电齿轮箱
CN109654182B (zh) 无级变速器
CN211259501U (zh) 一种多速比复合输出减速器
CA2933999A1 (en) Planetary gear, wind generator comprising a planetary gear and use of a planetary gear
WO2024037114A1 (zh) 一种平行驱动装置
US8091445B1 (en) Offset compound gear inline two-speed drive
JP2013002601A (ja) ウォームギア減速機構の減速比を備えるエピサイクリック歯車列の変速装置
US11619289B2 (en) Continuously variable transmission
CN209892700U (zh) 一种无级变速器
CN209398799U (zh) 一种大速比高速行星轮系减速器结构
JP2010196772A (ja) 多段式遊星歯車変速装置
CN219737969U (zh) 一种基于行星变速的超高速转镜装置
JP2008208959A (ja) 増速機およびそれを用いた風力発電装置
CN206280441U (zh) 齿轮箱及风电机组
CN203822550U (zh) 风力发电机传动装置及风力发电机
US20190017576A1 (en) Power transmission device
CN220791992U (zh) 一种风电偏航变桨减速机
CN117366174A (zh) 一种行星轮系和齿轮变速装置、风力发电机组
CN220956628U (zh) 一种微型电机用减速器
CN115355285A (zh) 齿轮箱、传动链及风力发电机组
CN214404623U (zh) 一种精密传动行星齿轮减速器

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 22943454

Country of ref document: EP

Kind code of ref document: A1