A wind turbine gearbox and a gearbox input flange

Abstract

The application provides a wind power gear box, which comprises a front box body and a rear box body connected with each other, a primary planetary carrier is fixedly connected with the inner wall of the front box body; the gear box is provided with at least a primary planetary transmission mechanism comprising a primary inner gear ring, a primary planetary gear, a primary planetary carrier and a primary sun gear, an outer spline is formed on the outer peripheral wall of the primary inner gear ring, and an input flange is sleeved on the outer spline, one end of the input flange is used for being fixedly connected with the tail end of a wind wheel main shaft, the inner wall of the other end of the input flange is provided with an inner spline matched with the outer spline, and a gap is formed between the inner spline and the outer spline, so that the input flange can float relative to the primary inner gear ring. The application provides a novel gear box adopting a thin-wall flange plus floating spline pair connection design at an input end, and the problem that the serious deflection deformation of a main shaft seriously affects the normal meshing of a primary gear pair after the main shaft is rigidly connected with a primary planetary carrier in a traditional full-integrated transmission chain gear box is solved, and the service life of the gear box is improved.

Description

TECHNICAL FIELD

[0001] The present application relates to the field of wind power technology, and particularly relates to a wind power gear box and a gear box input flange. BACKGROUND

[0002] With the competition of the wind power market, the price of wind power equipment is continuously reduced, and the wind turbine manufacturer must continuously reduce the manufacturing cost on the premise of ensuring the performance to meet the requirements. In the composition of the unit, the cost and performance of the transmission chain directly determine the cost and performance of the unit. The traditional wind turbine transmission chain is composed of hub, main shaft system, gear box, generator and other independent components, which need to be connected by couplings, elastic supports and other components.

[0003] To improve market competitiveness, the development trend of the wind turbine transmission chain is to tightly integrate the main shaft, main bearing, main bearing seat, gear box and generator into a whole structure, cancel the elastic support and part of the coupling components, and share the box structure, so as to reduce the number of components and shorten the length of the transmission chain, thereby achieving the purpose of reducing the cost. The unit of such structure is usually called a full-integrated transmission chain wind turbine. Referring to Figure 1 and 2 , at present, in the conventional full-integrated transmission chain, the gear box usually adopts a conventional planetary speed-up structure. In this structure, the input end of the primary planetary carrier is rigidly connected to the wind wheel main shaft as a whole by a certain number of bolts, and a large-diameter bearing is arranged on each side of the primary planetary carrier for support; the front box body of the gear box is rigidly connected to the wind wheel main shaft bearing seat as a whole by bolts; the rear box body of the gear box is rigidly connected to the generator stator shell as a whole; and the generator rotor is directly connected or connected through a coupling to the gear box output shaft.

[0004] Referring to Figure 1 , it can be seen that the existing full-integrated transmission chain structure has the following shortcomings:

[0005] 1. Due to the influence of the wind wheel gravity and working load, the wind wheel main shaft will produce deflection deformation during work. Since the gear box primary planetary carrier is rigidly connected to the tail end of the wind wheel main shaft by bolts (or bolts + pins), the deflection deformation of the wind wheel main shaft will be directly transmitted to the primary planetary carrier, causing the primary planetary carrier axis to be inclined and displaced, and further seriously damaging the meshing state of the primary planetary gear pair, affecting the service life of the primary planetary gear pair.

[0006] 2. In order to control the axial deflection and displacement of the primary planetary carrier, reduce the adverse effects of the deflection deformation of the main shaft of the wind wheel, and support and limit the primary planetary carrier at both ends. But because the added front support bearing of the planetary carrier is close to the tail end bearing of the main shaft of the wind wheel, in order to avoid bearing excessive deformation resistance of the main shaft, the planetary carrier support bearing can only choose a cylindrical roller bearing with large clearance value to accommodate part of the deformation amount transmitted by the main shaft. Because the bearing clearance value is large, the deflection of the main shaft of the wind wheel has a limited effect on the deflection and displacement of the primary planetary carrier, which also leads to complex transmission chain structure and difficult calculation and analysis.

[0007] 3. Because the main shaft of the wind wheel is rigidly connected with the primary planetary carrier, four large bearings are installed on the shaft system, which greatly increases the material cost.

[0008] 4. Because the main shaft of the wind wheel is rigidly connected with the primary planetary carrier, in order to ensure the normal work of the two bearings on the main shaft and the two bearings on the primary planetary carrier, the size precision and shape tolerance of the bearing installation shaft diameter of the main shaft and the primary planetary carrier, and the bearing seat installation hole of the front box body of the gear box and the gear box must be strictly controlled, which increases the processing difficulty and processing cost. SUMMARY

[0009] In view of the defects in the prior art, the gear box input flange and the wind power gear box provided by the present application at least solve the technical problem that the deflection deformation of the main shaft of the wind wheel affects the service life of the wind power gear box in the full integrated transmission chain structure of the existing wind turbine.

[0010] In order to achieve the above purpose, the present application realizes the technical scheme as follows:

[0011] The first aspect of the present application provides a wind power gear box, at least one primary planetary transmission mechanism is arranged in the gear box, the primary planetary transmission mechanism comprises a primary inner ring gear, a primary planetary gear, a primary planetary carrier and a primary sun gear, the primary inner ring gear is sleeved on the outer periphery of the primary sun gear and is in meshing transmission with the primary planetary gear;The gear box comprises a front box body and a rear box body connected with each other, and the primary planetary carrier is fixedly connected with the inner wall of the front box body;The outer periphery of the primary inner ring gear is sleeved with an input flange, and the outer periphery wall of the primary inner ring gear is provided with an external spline;The end of the input flange away from the rear box body is used for fixedly connecting with the tail end of the main shaft of the wind wheel, and the inner wall of the end of the input flange towards the rear box body is provided with an internal spline matched with the external spline, so as to spline the input flange with the primary inner ring gear, so that the main shaft of the wind wheel transmits torque to the primary planetary transmission mechanism through the input flange, and the internal spline and the external spline have a gap, so that the primary inner ring gear can float relative to the input flange.

[0012] Optionally, the input flange comprises a flange base and a flange sleeve coaxially connected, the flange base is used for fixed connection with the tail end of the main shaft of the wind wheel, and the inner wall of the flange sleeve is provided with the inner spline.

[0013] Optionally, the outer spline is provided with a first limiting piece and a second limiting piece on the two sides in the axial direction, and the first limiting piece and the second limiting piece are arranged on the input flange to axially limit the primary inner gear ring.

[0014] Optionally, the first limiting piece comprises a stopper arranged on the inner wall of the flange sleeve and close to the flange base, and the second limiting piece comprises a stopper plate detachably arranged on the flange sleeve away from the flange base.

[0015] Optionally, the front box body comprises an open part, a variable-diameter part and a connecting part connected in sequence, the open part is used for detachable connection with the bearing seat of the main shaft of the wind wheel at the end away from the variable-diameter part, the connecting part is used for detachable connection with the rear box body at the end away from the variable-diameter part, and the inner wall of the variable-diameter part is used for mounting the primary planetary carrier.

[0016] Optionally, the outer peripheral wall of the open part is provided with a groove, and the groove is distributed uniformly in the circumferential direction of the open part, so as to reduce the mass of the front box body.

[0017] In the second aspect of the present application, a gear box input flange is provided, the gear box is provided with at least a primary planetary transmission mechanism, the primary planetary transmission mechanism comprises a primary inner gear ring, a primary planetary gear, a primary planetary carrier and a primary sun gear, the primary inner gear ring is sleeved on the outer periphery of the primary sun gear and is in meshing transmission with the primary planetary gear; the input flange comprises a flange base and a flange sleeve coaxially connected; the flange base is used for fixed connection with the tail end of the external power input shaft; the inner wall of the flange sleeve is provided with an inner spline, so as to cooperate with the outer spline arranged on the outer wall of the primary inner gear ring, so that the external power input shaft transmits torque to the primary planetary transmission mechanism through the input flange, and the inner spline and the outer spline have a gap, so that the primary inner gear ring can float relative to the input flange.

[0018] Optionally, the input flange is further provided with a first limiting piece and a second limiting piece, so that the outer spline is clamped between the first limiting piece and the second limiting piece, and the primary inner gear ring is axially limited.

[0019] Optionally, the first limiting piece comprises a stopper arranged on the inner wall of the flange sleeve and close to the flange base, and the second limiting piece comprises a stopper plate detachably arranged on the flange sleeve away from the flange base.

[0020] Optionally, the flange base and the flange sleeve are connected by webs, and the webs are provided in plurality, and the plurality of webs are evenly distributed around the input flange in the circumferential direction.

[0021] From the above technical solutions, the beneficial effects of the present application are:

[0022] 1) The input flange of the gear box adopts a thin-walled structure and can automatically deform to compensate for the deflection deformation of the main shaft of the wind wheel; when the deflection deformation of the tail end of the main shaft of the wind wheel due to the working load is transmitted to the thin-walled flange, the thin-walled structure of the flange deforms accordingly, automatically adapts to the deflection of the main shaft, compensates for the deviation of the axis, and avoids transmitting the excessive deflection deformation of the main shaft to the rear end, causing the deformation of the primary planetary carrier, and further damaging the meshing state of the gear pair and reducing the service life of the planetary gear bearing;

[0023] 2) The floating connection of the input flange of the gear box and the outer spline of the primary inner gear ring further improves the meshing reliability of the planetary gear pair; when the thin-walled flange deforms to adapt to the deflection of the main shaft, the inner spline on the outer side deforms slightly and displaces accordingly, and the influence on the primary inner gear ring is further isolated through the isolation of the floating spline pair, ensuring that the gear pair is in good position;

[0024] 3) The gear box adopts a structure in which the gear ring and the sun gear rotate and the planetary carrier is fixed, which has good load sharing effect and simple and reliable lubrication; in the primary planetary transmission structure of the wind power gear box, in addition to the floating load sharing of the sun gear, the outer side of the primary inner gear ring is a floating spline that can displace radially, and can also provide load sharing effect for the multi-branch primary planetary gear during operation, so the load sharing effect of the primary planetary gear is very good, especially for the primary planetary transmission mechanism with a larger number of planetary gears, which can take advantage of the high power density of the planetary gear box; in addition, the planetary carrier in the primary planetary transmission structure of the wind power gear box is fixed on the front box body, and the lubricating oil path can be directly connected to the planetary gear bearing position, without considering the oil path sealing problem caused by the rotation of the planetary carrier, so the lubrication of the planetary gear is simple and reliable, and the service life is guaranteed;

[0025] 4) The gear box does not have a planetary carrier supporting bearing, which has a simple structure and low cost; since the primary planetary carrier in the primary planetary transmission structure of the wind power gear box is fixed on the front box body and does not need to rotate, it does not need to design a supporting bearing, which simplifies the manufacturing difficulty of the box body components, reduces the number of precision bearings used, and greatly reduces the cost. BRIEF DESCRIPTION OF DRAWINGS

[0026] In order to more clearly illustrate the technical solutions in the embodiments of the present application or the prior art, the following will briefly introduce the drawings needed in the specific embodiments or prior art description. In all the drawings, similar elements or parts are generally identified by similar reference signs. In the drawings, the elements or parts are not necessarily drawn according to the actual proportions.

[0027] Figure 1 A structural schematic diagram of a prior art full-integrated design wind turbine transmission chain;

[0028] Figure 2 A structural schematic diagram of an internal structure of a prior art wind turbine gearbox;

[0029] Figure 3 A structural schematic diagram of an improved full-integrated wind turbine transmission connection structure of the present application;

[0030] Figure 4 A structural schematic diagram of an internal structure of a wind turbine gearbox of the present application;

[0031] Figure 5 A Figure 4 A local enlarged view of A in FIG. 7;

[0032] Figure 6 A structural schematic diagram of an input flange;

[0033] Figure 7 A structural schematic diagram of a wind turbine gearbox of the present application;

[0034] Reference signs:

[0035] 1 - wind wheel main shaft, 2 - bearing seat, 3 - front box body, 4 - rear box body, 5 - first stage planetary transmission mechanism, 6 - second stage planetary transmission mechanism, 7 - second stage planetary transmission mechanism, 8 - generator, 9 - input flange;

[0036] 21 - main shaft front bearing, 22 - main shaft rear bearing, 31 - open part, 32 - variable diameter part, 33 - connecting part, 41 - output shaft, 51 - first stage inner ring gear, 52 - first stage planetary gear, 53 - first stage planetary carrier, 54 - first stage sun gear, 61 - second stage inner ring gear, 62 - second stage planetary gear, 63 - second stage planetary carrier, 64 - second stage sun gear, 71 - third stage inner ring gear, 72 - third stage planetary gear, 73 - third stage planetary carrier, 74 - third stage sun gear, 91 - flange base, 92 - flange sleeve, 93 - web;

[0037] 311 - groove, 531 - planetary carrier front bearing, 532 - planetary carrier rear bearing, 921 - first limiting member, 922 - second limiting member. DETAILED DESCRIPTION

[0038] The embodiments of the technical solutions of the present application will be described in detail below with reference to the drawings. The following embodiments are only used to more clearly illustrate the technical solutions of the present application, and therefore only serve as examples, but cannot limit the protection scope of the present application.

[0039] Please refer to Figures 3-5 and Figure 7 The present application provides a wind turbine gearbox, at least one stage planetary transmission mechanism 5 is arranged in the gearbox, the stage planetary transmission mechanism 5 includes a stage inner ring gear 51, a stage planetary gear 52, a stage carrier 53 and a stage sun gear 54, wherein the stage carrier 53 is sleeved on the outer periphery of the stage sun gear 54 and is rotatably connected therewith, the stage planetary gear 52 is rotatably arranged on the stage carrier 53 by bearings, and each stage planetary gear 52 is in meshing transmission with the stage sun gear 54, and the stage inner ring gear 51 is sleeved on the outer periphery of the stage sun gear 54 and is in meshing transmission with all the stage planetary gears 52. The gearbox includes a front gearbox 3 and a rear gearbox 4 connected with each other, the stage carrier 53 is fixedly connected with the inner wall of the front gearbox 3; the outer periphery of the stage inner ring gear 51 is sleeved with an input flange 9, and the outer peripheral wall of the stage inner ring gear 51 is provided with external splines; the end of the input flange 9 away from the rear gearbox 4 is used for fixedly connecting with the tail end of the wind turbine main shaft 1, and the inner wall of the end of the input flange 9 towards the rear gearbox 4 is provided with internal splines matched with the external splines, so as to facilitate the spline connection between the input flange 9 and the stage inner ring gear 51, and further make the wind turbine main shaft 1 transmit torque to the stage planetary transmission mechanism through the input flange 9, and the internal splines and the external splines have a gap, so that the stage inner ring gear 51 can float relative to the input flange 9. Specifically, the input end of the wind turbine gearbox adopts a thin-walled flange plus a floating spline pair, which isolates the influence of the deflection deformation of the main shaft and realizes the floating connection of the main shaft and the gearbox.

[0040] In work, the thin-walled flange deformation combined with the radial floating of the spline is relied on to compensate the axis deflection and offset of the wind turbine main shaft 1, isolate the meshing influence of the stage planetary gear pair, and ensure that the stage planetary gear pair maintains a good contact state in work. The stage planetary transmission mechanism 5 adopts an atypical structure, i.e. the ring gear and the sun gear rotate, and the carrier is fixed on the front gearbox 3. Since the carrier no longer needs large support bearings on both sides, the cost of the gearbox is directly reduced by a large margin; at the same time, the carrier is fixedly connected, the oil way is simple, and the lubrication of the planetary gear bearing is improved; since the main shaft and the gearbox are floatingly connected and there is no stage carrier 53 support bearing, the number of transmission chain shaft bearing matching shaft diameters and gearbox bearing mounting holes is reduced, the machining and assembly requirements are simplified, and the machining difficulty and cost are also reduced. By adopting the above structure, a new type of gearbox structure is formed. The full integration transmission chain of the new type of gearbox can improve the reliability of the unit, reduce the cost of the unit, and improve the competitiveness of the unit.

[0041] In the conventional planetary gear transmission structure of wind power, the gear ring is a fixed structure and cannot be uniformly loaded, the planet carrier is also not uniformly loaded due to being constrained by bearings, and only the sun gear is floating and has a certain load sharing effect. In the first-stage planetary transmission structure of the wind power gear box in the present project, in addition to the floating load sharing of the first-stage sun gear 54, the outer side of the first-stage inner gear ring 51 is a floating spline that can be radially displaced, and can also provide load sharing effect for the multiple split first-stage planetary gears in operation, so that the first-stage planetary gears 52 have very good load sharing effect, which is particularly beneficial to the use of a larger number of planetary gears in the first-stage planetary transmission mechanism, and can bring out the advantage of high power density of the planetary gear box.

[0042] In one embodiment, in the present gear box, the input component is a thin-walled flange plus a floating spline pair structure, one end of which is rigidly connected to the wind turbine main shaft 1 through bolts (or bolts + pins), and the other end is an inner spline that is gap-fitted with the outer spline of the outer circle of the first-stage inner gear ring 51 to realize floating connection. After the thin-walled flange plus floating spline pair connection is adopted, the gear ring and the sun gear rotate, while the planet carrier is fixed to the front box body 3 and does not need to be supported by bearings, so the bearing mounting hole on the front box body 3 is cancelled. The front box body 3 is rigidly connected to the main shaft bearing seat 2 with bolts to form an integral body; the second-stage and third-stage planetary structures are conventional planetary structures; the gear box output shaft 41 is floatingly connected to the sun gear of the third-stage planet at one end and is rigidly connected to the generator rotor at the other end or is connected through a coupling; and the rear box body 4 is rigidly connected to the generator stator shell.

[0043] In the above embodiment, the connection relationship of the wind power gear box in the full-integrated transmission chain is as follows: the hub (not marked in the figure) is rigidly connected to the wind turbine main shaft 1; the main shaft is provided with a main shaft front bearing 21 on the hub side and a main shaft rear bearing 22 on the gear box side; the main shaft front bearing 21 and the main shaft rear bearing 22 are both mounted on the bearing seat 2 of the wind turbine main shaft 1; the gear box input structure is composed of a thin-walled flange and an inner spline sleeve, wherein the thin-walled flange is the input flange 9 of the gear box; the thin-walled flange is rigidly connected to the main shaft through a plurality of connecting bolts or bolts + pins, and the inner spline sleeve at the rear end is floatingly connected to the outer spline of the outer circle of the first-stage inner gear ring 51; the front box body 3 is rigidly connected to the main shaft bearing seat 2 to form an integral body; after the speed is increased through the three-stage planetary gear pair, the sun gear of the third-stage planet is connected to the output shaft 41; the output shaft 41 is rigidly connected to the generator rotor through bolts; and the generator stator is rigidly connected to the gear box rear box body 4.

[0044] The working principle of the wind power gear box is as follows: all loads generated by the wind wheel are applied to the hub, and since the hub is directly rigidly connected with the main shaft, the wind wheel thrust, gravity, torque and lateral load from the hub end are all transmitted to the main shaft; since the thin-wall flange at the input end of the gear box is rigidly connected with the main shaft as a whole through a bolt set or a bolt + pin, the main shaft directly transmits the torque to the thin-wall flange at the input end of the gear box, and the remaining loads on the main shaft are transmitted to the main shaft bearing seat 2 through the front shaft bearing 21 and the rear shaft bearing 22 of the main shaft, and further transmitted to the rack; the rear end of the thin-wall flange has an inner spline sleeve, the inner spline sleeve is arranged in the outer spline gap on the outer circle of the first-level inner gear ring 51 in a clearance fit, and forms a floating spline pair; the torque of the thin-wall flange is transmitted to the first-level inner gear ring 51 through the inner spline sleeve. When the main shaft is loaded and deflected, the deflection is transmitted to the thin-wall flange, and since the thin-wall flange has low rigidity, the corresponding deformation is generated, the deflection of the main shaft is compensated, and the deflection is prevented from being transmitted to the first-level inner gear ring 51; at the same time, since the spline of the inner spline sleeve and the outer circle of the first-level inner gear ring 51 is in clearance fit, the first-level inner gear ring 51 can float radially, and the deflection of the main shaft is further isolated from the meshing influence of the first-level planetary gear, and the meshing of the first-level planetary gear pair is ensured; since the first-level planetary transmission mechanism adopts multi-branch planetary gear transmission, the first-level inner gear ring 51 can also reduce the uneven load coefficient of the multi-branch transmission of the first-level planetary gear, and greatly improve the meshing condition. At the same time, the first-level planet carrier 53 is fixed to the inner wall of the front box body 3, and the lubricating oil path of the planetary gear bearing can be conveniently arranged, the problem that the lubricating oil is difficult to enter the planetary gear bearing due to the rotation of the traditional planet carrier is avoided, and the lubrication of the first-level planetary gear 52 is greatly improved; the torque of the first-level inner gear ring 51 is transmitted to the second-level planet carrier 63 after speed increasing through the first-level planetary gear 52 and the first-level sun gear 54; the second-level planet carrier 63, the second-level sun gear 64, the second-level planetary gear 62 and the second-level inner gear ring 61 form the second-level planetary speed-increasing gear pair, and realize the second speed increase; the second-level sun gear 64 is connected with the third-level planet carrier 73 through the spline, and the torque is transmitted; the third-level planet carrier 73, the third-level inner gear ring 71, the third-level sun gear 74 and the third-level planetary gear 72 form the third-level planetary speed-increasing gear pair, and realize the third speed increase; the third-level sun gear 74 is connected with the output shaft 41 through the spline, the torque is transmitted, and the speed-increased torque is transmitted to the generator rotor through the output shaft 41 to drive the generator 8 to generate electricity.

[0045] The application provides a novel gearbox with a thin-wall flange and a floating spline pair connection at an input end, which changes the structure of a traditional full-integrated transmission chain wind power gearbox, overcomes the problem that the deflection deformation of a main shaft seriously affects the normal meshing of a first gear pair after the main shaft is rigidly connected with a first planetary carrier 53, and reduces the number of shafting bearings, the shaft diameter of bearing installation, and the machining precision requirement of a seat hole.

[0046] As a further improvement of the above-mentioned scheme, please refer to Figure 6 The input flange 9 comprises a coaxially connected flange base 91 and flange sleeve 92, the flange base 91 is fixedly connected with the tail end of the main shaft 1 away from the flange sleeve 92, and the inner wall of the flange sleeve 92 is provided with the inner spline. The input flange 9 of the gearbox adopts a thin-wall structure. The thickness of the central position (i.e. the flange base 91) of the thin-wall flange is increased to improve the rigidity, facilitate the bolt set (or bolt + pin) connection with the main shaft, and the outermost side (i.e. the flange sleeve 92) of the flange is provided with an inner spline structure; the connecting wall plate between the central high-rigidity part and the inner spline part is designed as a thin-wall structure, and the thin-wall structure design only needs to transmit the working torque to the spline pair. When the deflection of the tail end of the main shaft caused by the working load is transmitted to the thin-wall flange, the thin-wall structure of the flange deforms correspondingly, automatically adapts to the deflection of the main shaft, and realizes the compensation of the deviation of the axis. The deflection deformation of the main shaft is avoided from being transmitted to the tail end, the deformation of the first planetary carrier 53 is avoided, and the meshing state of the gear pair and the bearing life of the planetary gear are avoided from being reduced.

[0047] As a further improvement of the above-mentioned scheme, the two sides of the outer spline in the axial direction are respectively provided with a first limiting piece 921 and a second limiting piece 922, and the first limiting piece 921 and the second limiting piece 922 are arranged on the input flange 9 and used for axially limiting the first inner tooth ring 51. For example, the first limiting piece 921 comprises a stopper arranged on the inner wall of the flange sleeve 92 and close to the flange base 91, and the second limiting piece 922 comprises a stopper plate detachably arranged on the side of the flange sleeve 92 away from the flange base 91.

[0048] As a further improvement of the above-mentioned scheme, please refer to Figure 5 and 7The front box body 3 comprises an open part 31, a variable-diameter part 32 and a connecting part 33 connected in sequence; the open part 31 is used for detachable connection with the bearing seat 2 of the wind wheel main shaft 1 at one end away from the variable-diameter part 32; the connecting part 33 is used for detachable connection with the rear box body 4 at one end away from the variable-diameter part 32; and the inner wall of the variable-diameter part 32 is used for mounting the primary planetary carrier 53. Preferably, a groove 311 is formed on the outer peripheral wall of the open part 31, and a plurality of grooves 311 are uniformly distributed in the circumferential direction of the open part 31, so as to reduce the mass of the front box body 3.

[0049] The application further provides a gear box input flange which can be applied to the above-mentioned wind power gear box. The gear box is provided with at least a primary planetary transmission mechanism 5, which comprises a primary inner ring gear 51, a primary planetary gear 52, a primary planetary carrier 53 and a primary sun gear 54. The primary inner ring gear 51 is sleeved on the outer periphery of the primary sun gear 54 and is in meshing transmission with the primary planetary gear 52. The input flange 9 comprises a flange base 91 and a flange sleeve 92 which are coaxially connected. The flange base 91 is used for fixed connection with the tail end of an external power input shaft at one end away from the flange sleeve 92. An inner spline is formed on the inner wall of the flange sleeve 92, which is matched with an outer spline arranged on the outer wall of the primary inner ring gear 51, so that the external power input shaft transmits torque to the primary planetary transmission mechanism through the input flange 9. The input flange 9 can float relative to the primary inner ring gear 51 because there is a gap between the inner spline and the outer spline. The side of the input flange 9 is designed as a thin-walled inner spline, and the outer circle of the primary inner ring gear 51 is machined with an outer spline. The outer spline and the thin-walled inner spline of the input flange 9 are matched with a gap to realize floating connection. When the main shaft is deflected and displaced under the action of load, the spline pair of the floating connection can produce corresponding radial displacement, so as to isolate the influence of the deformation and displacement of the main shaft on the primary inner ring gear 51 and ensure that the meshing of the gear pair is in a good position. In addition, the sleeve on the outer side of the inner spline is designed as a thin wall, which can be deformed to a certain extent when the load is large, so as to increase the meshing area of the spline teeth, reduce the contact stress of the spline tooth surface and improve the reliability.

[0050] As a further improvement of the above-mentioned scheme, the input flange 9 is further provided with a first limiting piece 921 and a second limiting piece 922, so that the outer spline is clamped between the first limiting piece 921 and the second limiting piece 922, and further used for axially limiting the primary inner ring gear 51. For example, the first limiting piece 921 comprises a stopper arranged on the inner wall of the flange sleeve 92 and close to the side of the flange base 91, and the second limiting piece 922 comprises a stopper plate which is detachably arranged on the side of the flange sleeve 92 away from the flange base 91.

[0051] As a further improvement of the above-mentioned scheme, the flange base 91 and the flange sleeve 92 are connected by webs 93, and the webs 93 are provided in plurality, and the plurality of webs 93 are evenly distributed around the input flange 9. According to the requirement, a plurality of evenly distributed through holes can also be provided on the thin-walled web 93, and the through holes can have various shapes; at the same time, the through holes can further reduce the weight of the flange, increase the flexibility of the flange, and improve the deformation compensation capability. The middle part of the input flange 9 is designed with thin-walled webs 93, which has the characteristics of large flexibility and easy deformation, and can automatically deform to compensate for the deflection change of the main shaft. When the tail end of the main shaft deflects due to the working load, the thin-walled web 93 structure of the flange deforms correspondingly when the deflection change is transmitted to the thin-walled spline flange, and automatically adapts to the deflection of the main shaft to realize the compensation of the deviation of the axis line. Avoiding the transmission of the large deflection deformation of the main shaft to the rear end, causing the deformation of the primary planetary carrier 53, and further damaging the meshing state of the gear pair and reducing the bearing life of the planetary gear.

[0052] Finally, it should be noted that: the above embodiments are only used to illustrate the technical solutions of the present application, and not to limit them; although the present application has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that: it can still modify the technical solutions recorded in the foregoing embodiments, or make equivalent replacement to part or all of the technical features; and these modifications or replacements do not make the essence of the corresponding technical solutions deviate from the scope of the technical solutions of the embodiments of the present application, and they should be covered in the scope of the claims and the specification of the present application.

Claims

1. A wind turbine gearbox, at least one stage planetary transmission mechanism (5) is arranged in the gearbox, the stage planetary transmission mechanism (5) comprises a stage inner ring gear (51), a stage planetary gear (52), a stage carrier (53) and a stage sun gear (54), the stage inner ring gear (51) is sleeved on the outer periphery of the stage sun gear (54) and is in meshing transmission with the stage planetary gear (52); characterized in that, the gearbox comprises a front gearbox (3) and a rear gearbox (4) connected with each other, the stage carrier (53) is fixedly connected with the inner wall of the front gearbox (3); the outer periphery of the stage inner ring gear (51) is sleeved with an input flange (9), and the outer peripheral wall of the stage inner ring gear (51) is provided with external splines; the end of the input flange (9) away from the rear gearbox (4) is used for being fixedly connected with the tail end of a wind wheel main shaft (1), and the inner wall of the end of the input flange (9) towards the rear gearbox (4) is provided with internal splines matched with the external splines, so as to facilitate the spline connection of the input flange (9) and the stage inner ring gear (51), and further make the wind wheel main shaft (1) transmit torque to the stage planetary transmission mechanism (5) through the input flange (9), and the internal splines and the external splines have a gap, so that the stage inner ring gear (51) can float relative to the input flange (9).

2. A wind turbine gearbox according to claim 1, characterised in that The input flange (9) comprises a flange base (91) and a flange sleeve (92) connected coaxially, the end of the flange base (91) away from the flange sleeve (92) is used for being fixedly connected with the tail end of the wind wheel main shaft (1), and the inner wall of the flange sleeve (92) is provided with the internal splines.

3. A wind turbine gearbox according to claim 2, characterised in that The two sides of the external splines in the axial direction are respectively provided with a first limiting piece (921) and a second limiting piece (922), and the first limiting piece (921) and the second limiting piece (922) are both arranged on the input flange (9) and used for axially limiting the stage inner ring gear (51).

4. A wind turbine gearbox according to claim 3, characterised in that The first limiting piece (921) comprises a stopper arranged on the inner wall of the flange sleeve (92) and close to the flange base (91), and the second limiting piece (922) comprises a stopper plate detachably arranged on the side of the flange sleeve (92) away from the flange base (91).

5. A wind turbine gearbox according to any of claims 2-4, characterised in that The front gearbox (3) comprises an open part (31), a variable-diameter part (32) and a connecting part (33) connected in sequence; the end of the open part (31) away from the variable-diameter part (32) is used for being detachably connected with a bearing seat (2) of the wind wheel main shaft (1); the end of the connecting part (33) away from the variable-diameter part (32) is used for being detachably connected with the rear gearbox (4); and the inner wall of the variable-diameter part (32) is used for mounting the stage carrier (53).

6. A wind turbine gearbox according to claim 5, characterised in that The outer peripheral wall of the open part (31) is provided with grooves (311), and a plurality of grooves (311) are uniformly distributed in the circumferential direction of the open part (31), so as to reduce the mass of the front gearbox (3).

7. A gear box input flange, at least one stage planetary transmission mechanism (5) is arranged in the gear box, the stage planetary transmission mechanism (5) comprises a stage inner ring gear (51), a stage planetary gear (52), a stage carrier (53) and a stage sun gear (54), the stage inner ring gear (51) is sleeved on the outer periphery of the stage sun gear (54) and is in meshing transmission with the stage planetary gear (52); characterized in that, the input flange (9) comprises a flange base (91) and a flange sleeve (92) connected coaxially; the flange base (91) is fixedly connected with the tail end of an external power input shaft at an end away from the flange sleeve (92); an inner spline is formed on the inner wall of the flange sleeve (92) to cooperate with an outer spline arranged on the outer wall of the stage inner ring gear (51), so that the external power input shaft transmits torque to the stage planetary transmission mechanism (5) through the input flange (9), and the inner spline and the outer spline have a gap therebetween to enable the stage inner ring gear (51) to float relative to the input flange (9).

8. A gearbox input flange according to claim 7, wherein, first and second limiting members (921, 922) are further arranged on the input flange (9) to clamp the outer spline between the first and second limiting members (921, 922), thereby axially limiting the stage inner ring gear (51).

9. A gearbox input flange according to claim 8, wherein, The first limiting member (921) comprises a stopper arranged on the inner wall of the flange sleeve (92) and close to the flange base (91), and the second limiting member (922) comprises a stopper plate detachably arranged on the side of the flange sleeve (92) away from the flange base (91).

10. A gearbox input flange according to claim 7, wherein, The flange base (91) and the flange sleeve (92) are connected through webs (93), and a plurality of webs (93) are arranged, and the plurality of webs (93) are evenly distributed around the input flange (9) in the circumferential direction.

Images