CN111994776A

CN111994776A - Pitching rotating mechanism and blade hoisting tool

Info

Publication number: CN111994776A
Application number: CN202010870781.5A
Authority: CN
Inventors: 程伟; 方晶; 李红峰; 黄可唯; 黄建伟; 邓艳
Original assignee: CHENGDU SHIWEI TECHNOLOGY CO LTD; Fujian Goldwind Technology Co ltd
Current assignee: CHENGDU SHIWEI TECHNOLOGY CO LTD; Fujian Goldwind Technology Co ltd
Priority date: 2020-08-26
Filing date: 2020-08-26
Publication date: 2020-11-27
Anticipated expiration: 2040-08-26
Also published as: CN111994776B

Abstract

The utility model provides a every single move rotary mechanism and blade hoist and mount frock, every single move rotary mechanism includes braced frame and drive unit, drive unit is including rotationally setting up the ring gear on braced frame, be located the inboard driving gear of ring gear and arrange the driven gear between the inner periphery of driving gear periphery and ring gear, driven gear can respectively with ring gear and driving gear meshing, in order to transmit the rotary driving power of driving gear for the ring gear, the ring gear is used for fixed connection to the blade anchor clamps, in order to drive the blade anchor clamps along with the ring gear is rotatory, under the drive of driving gear, driven gear rotates and transmits the rotary driving power of driving gear for the ring gear, the ring gear will drive the blade anchor clamps and rotate together to the oar bearing alignment of becoming with wheel hub, and need not additionally to use the barring mechanism to carry out barring.

Description

Pitching rotating mechanism and blade hoisting tool

Technical Field

The utility model belongs to the technical field of wind power generation, especially, relate to a every single move rotary mechanism and have this every single move rotary mechanism's blade hoist and mount frock.

Background

With the increasing single-machine capacity of wind generating sets, the size of blades of the wind generating sets is gradually increased, for example, the length of the blades of offshore wind generating sets exceeds 90 meters, and the weight of the blades exceeds 35 tons.

The hub needs to be rotated by means of the barring structure in the traditional blade installation process, so that a variable pitch bearing of the hub can correspond to the position of a blade flange, along with the increase of the blade, the load required to be borne by the traditional barring structure is also larger and larger, and therefore the end cover structure (connected with the barring) of the generator deforms in the barring process, and normal operation of a unit is affected.

Because blade length is overlength, trefoil installation is because the restriction of installation ship, it has very big risk to stand up, for example in the installation of above-mentioned blade, the blade hoist and mount frock of use can take the blade to carry out the small-angle rotation, for example rotatory 30, consequently need the loop wheel machine to take blade hoist and mount frock barring to carry out the rotation of large angle, but this kind of mode has very big potential safety hazard, for example, the loop wheel machine takes blade hoist and mount frock barring in-process, the influence of lifting hook in-process acceleration is put down, probably lead to the lifting hook to collide with the blade, perhaps because the loop wheel machine maloperation produces extra pulling force and makes the blade slide out from the grip opening because the blade hoist frock produces extra pulling force to the blade.

The installation of first blade is accomplished at above-mentioned blade hoist and mount frock and under the condition that needs the centre gripping second blade, need exchange the position of the blade grip block of centre gripping mouth and apex grip block usually, and this installation complex operation is wasted time and energy.

Disclosure of Invention

One of the main objects of the present disclosure is to provide a pitch and rotation mechanism to be able to clamp the blades for rotation together without additional use of a barring mechanism during blade installation.

Aiming at the above purpose, the present disclosure provides the following technical solutions:

one aspect of the present disclosure provides a pitching rotation mechanism, pitching rotation mechanism includes braced frame and drive unit, drive unit including rotationally set up in braced frame is last the ring gear, be located the inboard driving gear of ring gear and arrange in the driven gear of driving gear periphery, driven gear can respectively with the ring gear with the driving gear meshing, in order with the rotary drive power transmission of driving gear is given the ring gear, the ring gear is used for fixed connection to the blade anchor clamps, in order to drive the blade anchor clamps along with the ring gear is rotatory.

In an exemplary embodiment of the present disclosure, the driven gear is provided in plurality, and the plurality of driven gears are disposed at equal angular intervals on an outer circumference of the driving gear.

Optionally, a plurality of fastener mounting holes are provided in the gear ring, such that the gear ring can be fixedly connected with the blade clamp via fasteners.

Further, a flange is formed to protrude outward from a side of the ring gear facing the blade jig, and the plurality of fastener mounting holes are formed on the flange.

According to another exemplary embodiment of the present disclosure, a counterweight frame structure is disposed on one end side of the supporting frame, which is far away from the driving unit, and at least one of an electric control cabinet, a storage battery, a frequency conversion cabinet and a counterweight block is disposed on the counterweight frame structure.

Further, the number of the driven gears is 2-6, and the driven gears are symmetrically arranged around the circumference of the driving gear.

On the other hand of this disclosure, provide a blade hoist and mount frock, blade hoist and mount frock includes every single move rotary mechanism and blade anchor clamps, blade anchor clamps include the girder and set up in the blade centre gripping unit at girder both ends, every single move rotary mechanism connect in the girder can drive the girder follows the ring gear rotates together, blade centre gripping unit includes centre gripping subassembly, lower centre gripping subassembly and presss from both sides a mouthful regulating unit, it connects to press from both sides a mouthful regulating unit go up centre gripping subassembly and down between the centre gripping subassembly, be used for adjusting go up the centre gripping subassembly with the size of the centre gripping mouth that the centre gripping subassembly formed down.

Further, the upper clamping assembly comprises a pressing arm, an upper vertical arm and an angle adjusting unit, the upper vertical arm extends downwards from one end of the pressing arm, a pivot shaft is arranged at the upper part of the upper vertical arm, the pressing arm is connected to the upper vertical arm through the pivot shaft, the angle adjusting unit comprises a second telescopic driving mechanism, the second telescopic driving mechanism is a second telescopic oil cylinder, the first end of the second telescopic oil cylinder is hinged with the lower part of the upper vertical arm and can be telescopic, and the second end of the second telescopic oil cylinder is hinged with the end part of the pressing arm so as to drive the pressing arm to pivot around the pivot shaft; and/or the lower clamping assembly comprises a bearing arm and a lower vertical arm extending upwards from one end of the bearing arm, and the lower vertical arm is connected with the upper vertical arm, so that the upper clamping assembly and the lower clamping assembly form a space for clamping the blade.

Preferably, blade hoist and mount frock still includes first locking Assembly for with the upper standing arm is for the lower standing arm locking, first locking Assembly includes: a first locking member mounted on one of the lower and upper vertical arms; a second locking member mounted on the other of the lower vertical arm and the upper vertical arm and opposed to the first locking member, having a locked position in which the second locking member is engaged with the first locking member to lock the relative position of the upper clamp assembly and the lower clamp assembly, and an unlocked position in which the second locking member is disengaged from the first locking member so that the upper vertical arm can move relative to the lower vertical arm; and a first driving member connected to the second locking member for driving the second locking member to move to at least one of the locking position and the unlocking position.

In another exemplary embodiment of the present disclosure, the first locking member is a long rack gear installed on the lower stand arm and extending in a direction in which the upper stand arm moves relative to the lower stand arm; the second locking member is a short rack mounted on the upper boom to be opposed to the long rack and movable in a direction perpendicular to a direction in which the upper boom moves relative to the lower boom by the drive of the first drive member, which is a telescopic cylinder, so that the short rack and the long rack are engaged with each other in the lock position.

Preferably, the blade hoisting tool further comprises a second locking assembly for locking the pressing arm relative to the upper standing arm, and the second locking assembly comprises: a stopper for limiting the retraction of the first end of the second telescopic cylinder, the stopper being a locking wedge having a locking position and an unlocking position, the locking wedge having an inclined surface, the inclined surface of the locking wedge abutting against a lower portion of the first end of the second telescopic cylinder in a direction in which the first end of the second telescopic cylinder is retracted to limit the retraction of the first end of the second telescopic cylinder, the locking wedge disengaging from the first end of the second telescopic cylinder in the unlocking position; the second locking assembly further includes a second drive member mounted on the hold down arm for driving the locking wedge to move to at least one of the locked position and the unlocked position; the second locking assembly further comprises a support frame, the support frame is installed on the upper portion of the upper vertical arm, the locking wedge block is installed on the support frame and can move along the direction close to or far away from the first end of the second telescopic oil cylinder, a groove is formed in the support frame and extends along the telescopic stroke of the first end of the second telescopic oil cylinder to guide the motion track of the first end of the second telescopic oil cylinder, and after the first end of the second telescopic oil cylinder retracts, the bottom of the groove supports the first end.

Further, the second locking assembly includes: a stopper for restricting retraction of the first end of the second telescopic cylinder, the stopper including: a baffle mounted on the upper boom and disposed on a telescopic path of the first end of the second telescopic cylinder; the eccentric wheel is arranged on the pressing arm and can rotate to a locking position and an unlocking position relative to the pressing arm, the eccentric wheel abuts against the baffle plate at the locking position so as to limit the extension and contraction of the first end of the second telescopic oil cylinder, and the eccentric wheel is separated from the baffle plate at the unlocking position so as to enable the first end of the second telescopic oil cylinder to extend and contract; the eccentric wheel comprises a long diameter end and a short diameter end, the long diameter end rotates to the baffle plate and abuts against the baffle plate in the locking position, and the short diameter end rotates to the baffle plate and is separated from the baffle plate in the unlocking position; the second locking assembly further includes a third drive member mounted on the hold down arm for driving the eccentric to at least one of the locked and unlocked positions.

The pitching rotating mechanism and the blade hoisting tool provided by the disclosure have the following beneficial effects: under the drive of the driving gear, the driven gear rotates and transmits the rotary driving force of the driving gear to the gear ring, the gear ring drives the blade clamp to rotate together to be aligned with a variable pitch bearing of the hub, and the additional turning mechanism is not needed to be used for turning the hub in the blade installation process.

Drawings

The above and/or other objects and advantages of the present disclosure will become more apparent from the following description of the embodiments taken in conjunction with the accompanying drawings, in which:

FIG. 1 is a diagram illustrating a portion of a blade lifting tool provided by an exemplary embodiment of the present disclosure.

Fig. 2 is an enlarged view of a portion a in fig. 1.

FIG. 3 is a block diagram of a blade clamp provided in accordance with an embodiment of the present disclosure.

Fig. 4 shows an exploded view of the blade holding unit of fig. 3.

Fig. 5 shows a perspective view of the internal structure of the blade holding unit in fig. 4.

Fig. 6 shows an exploded view of the blade holding unit in fig. 4.

Fig. 7 shows an enlarged view of the mobile locking assembly of fig. 4.

Figures 8, 9 and 10 show schematic views of the process of the compression arm locking assembly locking the compression arm relative to the upper stand arm.

Fig. 11 is a structural view of a blade holding unit according to another embodiment.

FIG. 12 illustrates a schematic view of a blade clamp according to an exemplary embodiment of the present disclosure.

FIG. 13 shows a schematic view of the blade clamp of FIG. 12 in a state before it is used for pitching a blade.

FIG. 14 illustrates a schematic view of the blade clamp of FIG. 12 after being used to pitch a blade.

Detailed Description

Example embodiments will now be described more fully with reference to the accompanying drawings. However, it should not be understood that the aspects of the present disclosure are limited to the embodiments set forth herein. The same reference numerals in the drawings denote the same or similar structures, and thus their detailed description will be omitted.

In one aspect of the present disclosure, a blade hoisting tool is provided, which includes a pitch rotation mechanism and a blade clamp 100, wherein the pitch rotation mechanism is used to drive the blade clamp 100 to perform pitch rotation in the air so as to perform attitude adjustment in the air, thereby adjusting the pitch rotation attitude of the clamped blade to align with a pitch bearing.

FIG. 1 is a diagram illustrating a portion of a blade lifting tool provided by an exemplary embodiment of the present disclosure. Fig. 2 is an enlarged view of a portion a in fig. 1.

As shown in fig. 1, a blade lifting tool according to an exemplary embodiment of the present disclosure includes a hanger 200 and a pitch rotating mechanism connected below the hanger 200, and may further include a blade clamp 100 shown in fig. 3. The blade clamp 100 is connected to the pitch rotation mechanism so that the blade clamp is driven to perform a pitch operation by the pitch rotation mechanism, thereby adjusting the pitch angle of the clamped blade.

Referring to fig. 1 and 2, the pitch rotation mechanism may include a support frame 410 and a driving unit including a ring gear 610 rotatably provided on the support frame 410, a driving gear 620 located inside the ring gear 610, and a driven gear 630 disposed at an outer periphery of the driving gear 620, the driven gear 630 being capable of being engaged with the ring gear 610 and the driving gear 620, respectively, to transmit a rotational driving force of the driving gear 620 to the ring gear 610, the ring gear 610 being configured to be fixedly coupled to the blade jig 100 to rotate the blade jig 100 along with the ring gear 610.

The ring gear 610 is annular and provided with teeth on an inner circumferential surface, the driving gear 620 has an outer diameter smaller than an inner diameter of the ring gear 610 and is coaxially arranged with the ring gear 610, and the driven gear 630 is arranged between the ring gear 610 and the driving gear 620 while being engaged with the ring gear 610 and the driving gear 620.

The ring gear 610 may be bearing-mounted on the support frame 410 so as to be rotatable with respect to the support frame 410. In other words, the bearing outer race may be fixedly mounted to the support frame 410, and the ring gear 610 may be fixed to an inner circumferential surface of the bearing inner race. Alternatively, the ring gear 610 may be formed integrally with the bearing inner race.

As shown in fig. 2, one side of the supporting frame 410 is provided with a protruding ring protruding outwards, and the ring gear 610 can be connected in the protruding ring through a bearing, that is, a bearing inner ring can be sleeved on the outer circumference of the ring gear 610, and a bearing outer ring is nested inside the protruding ring, so that the ring gear 610 can be connected on the supporting frame 410 through a bearing, and the ring gear 610 can rotate relative to the supporting frame 410, but not limited thereto. It will be appreciated that the support frame 410 may also be provided with a through hole for receiving the ring gear 610, and the ring gear 610 may be rotatably disposed in the through hole by a bearing.

In this embodiment, the driving gear 620 may serve as a driving unit of the pitch rotation mechanism, the driving gear 620 may transmit a rotation driving force to the gear ring 610 through the driven gear 630, that is, the rotation of the driving gear 620 may provide a power for rotating the gear ring 610, and the gear ring 610 may be connected to the blade clamp 100 to rotate the blade clamp 100. For example, but not limiting of, the ring gear 610 may rotate the blade clamp 100 in the air through 360 °.

Pitching rotation, which is described in this specification, means rotating the blade clamp 100 such that the angle of the length direction of the blade with respect to the horizontal plane changes, and pitching rotation is rotating the blade clamp 100 or rotating a part of the blade clamp 100 such that the blade turns in the circumferential direction.

Specifically, referring to fig. 2, a plurality of driven gears 630 may be disposed on the outer periphery of the driving gear 620, for convenience of description, only 4 driven gears 630 are taken as an example for illustration in the present embodiment, but not limited thereto, the number of the driven gears 630 may also be 1, 2, 3, 5, and the like, and the number of the driven gears 630 may be selected according to actual needs.

The 4 driven gears 630 may be disposed at an outer circumference of the driving gear 620 and engaged with the driving gear 620, the ring gear 610 is sleeved at an outer circumference of the driving gear 620 and may be coaxially disposed with the driving gear 620, gear teeth are disposed at an inner side of the ring gear 610, and the gear teeth of the 4 driven gears 630 may be engaged with the gear teeth of the ring gear 610, that is, the driven gears 630 are disposed between the ring gear 610 and the driving gear 620 and simultaneously engaged with the ring gear 610 and the driving gear 620, so as to transmit a driving force on the driving gear 620 to the ring gear 610 and drive the blade clamp 100 to rotate. In this embodiment, the 4 driven gears 630 may be identical, and the driving gear 620 may be driven by a motor, for example, but not limited to, the motor may be disposed on a side of the driving gear 620 facing away from the blade clamp 100. It is understood that the driven gear 630 is the same in the present embodiment, and the driving gear 620 and the ring gear 610 are coaxially disposed for the description, but not limited thereto, and in the case that the plurality of driven gears 630 are different, the driving gear 620 and the ring gear 610 will not be coaxial.

Further, 4 pivot shafts may be disposed on a circumference outside the driving gear 620, 4 driven gears 630 may be rotatably disposed on the 4 pivot shafts, respectively, and the 4 pivot shafts may be supported by the support frame 410. Alternatively, the 4 pivot axes may be spaced at equal angular intervals to provide more uniform force transfer between the drive gear 620 and the ring gear 610. Of course, the 4 driven gears 630 may be arranged symmetrically with respect to the line where the horizontal diameter of the driving gear 620 is located, so as to improve the vertical load-bearing capacity of the pitch rotation mechanism.

With continued reference to fig. 2, the end of the gear ring 610 facing the blade clamp 100 may be provided with a plurality of first fastener mounting holes 611 through which fasteners pass, and the blade clamp 100 may be provided with second fastener mounting holes 611 matching the first fastener mounting holes 611, and the fasteners may pass through and fasten both the first fastener mounting holes 611 and the second fastener mounting holes, and the blade clamp 100 may be attached to the pitch and rotation mechanism. Of course, an outer flange formed by an outward turned edge may be provided at an end of the ring gear 610 facing the blade fixture 100, and the first fastener mounting hole 611 may be provided on the outer flange, and the present embodiment is applicable to a case where the non-gear portion of the ring gear 610 has a small size in the radial direction of the ring gear 610 and the diameter of the fastener is large, but is not limited thereto, and is also applicable to a case where the non-gear portion of the ring gear 610 has a large size in the radial direction of the ring gear 610.

Referring to fig. 3, the blade clamp 100 includes a girder 120 and

blade clamping units

110, 130 provided at both ends of the girder 120. A main beam flange 121 is provided at the middle of the main beam 120, and a second fastener mounting hole is provided on the main beam flange 121, which can be matched with the first fastener mounting hole. After the blade clamp 100 and the pitch rotation mechanism are assembled, that is, after the gear ring 610 is connected to the main beam flange 121 through the fastener, the blade clamp 100 can rotate together with the gear ring 610 under the driving of the pitch rotation mechanism, so that the pitch attitude of the blade clamped by the blade clamp 100 can be adjusted in the air, and the blade can be accurately butted with the hub.

The center of the main beam flange 121 may be provided with a positioning pin 122, the center of the driving gear 620 is provided with a through hole matching with the positioning pin 122, and the positioning pin 122 may be inserted into the through hole of the driving gear 620, so that when the blade clamp 100 is assembled with the pitch rotation mechanism, the two may be accurately aligned, thereby improving the assembly efficiency.

As shown in fig. 3, the blade holding unit 110 and the blade holding unit 130 are respectively used for holding a blade tip portion and a blade root portion of the blade, and thus may be referred to as a blade tip holding unit and a blade root holding unit, respectively. The blade holding unit 110 and the blade holding unit 130 have substantially the same structure, except that the size adjustment range of the holding opening is different. Therefore, in the following description, only the structure of the blade holding unit 110 will be described.

The blade clamping unit 110 comprises an upper clamping assembly 140, a lower clamping assembly 150 and a clamping opening adjusting unit 115, the clamping opening adjusting unit 115 is connected between the upper clamping assembly 140 and the lower clamping assembly 150 and used for adjusting the size of a clamping opening formed by the upper clamping assembly 140 and the lower clamping assembly 150, and the clamping opening adjusting unit 115 can adjust the size of a clamping opening formed by the upper clamping assembly 140 and the lower clamping assembly 150, so that the blade clamping unit is suitable for clamping blades with different sizes.

Specifically, the blade clamping unit 110 may further include a first locking member 116 for locking the nip adjusting unit 115 after the nip adjusting unit 115 adjusts the size of the nip to an appropriate size, thereby preventing the upper and

lower clamping members

140 and 150 from moving relative to each other.

The upper clamp assembly 140 includes a pressing arm 111 and an upper standing arm 112 extending downward from one end of the pressing arm 111, and the pressing arm 111 is pivotable with respect to the upper standing arm 112. Specifically, referring to fig. 4, the pivoting end of the pressing arm 111 is pivoted to the upper standing arm 112, and when it is desired to load the blade, the free end of the pressing arm 111 is lifted up, and after the blade is loaded in place, the free end of the pressing arm 111 is rotated downward again to clamp the blade. The blade holding unit 110 according to the embodiment of the present disclosure may further include an angle adjusting unit 117 and a second locking assembly 118. The angle adjusting unit 117 is used to adjust the pivoting angle of the pressing arm 111, and the second locking assembly 118 is used to lock the pressing arm 111.

The lower clamp assembly 150 includes a support arm 113 and a lower standing arm 114 extending upward from one end of the support arm 113, and the lower standing arm 114 is connected to the upper standing arm 112, thereby forming a space (i.e., a clamping opening) for clamping the blade with the lower clamp assembly through the upper clamp assembly 140. The nip adjusting unit 115 is connected between the upper standing arm 112 and the lower standing arm 114, and is used for driving the upper clamping assembly to move relative to the lower clamping assembly, so as to adjust the distance between the pressing arm 111 and the supporting arm 113, and thus adjust the size of the nip. A first locking assembly 116 is used to lock the upper upright arm 112 relative to the lower upright arm 114. A second locking assembly 118 is used to lock the hold down arm 111 relative to the upper stand arm 112.

According to the blade clamp 100 of the exemplary embodiment of the present disclosure, a clamping space (i.e., a clamping port) having a "C" shape or a "T" shape is formed by the upper and lower clamping members, the pressing arm 111 and the supporting arm 113 form two clamp legs for clamping opposite surfaces of the blade, and the upper and lower standing

arms

112 and 114 constitute a telescopic standing arm connected between the pressing arm 111 and the supporting arm 113. The clamping range of the blade is adjusted to a large extent by relatively moving the upper vertical arm 112 and the lower vertical arm by the clamping port adjusting unit 115, and the pressing arm 111 is driven to rotate relative to the upper vertical arm 112 by the angle adjusting unit 117 to further adjust the magnitude of the clamping force for clamping the blade. Specifically, the pressing arm 111 may be rotated counterclockwise to open to increase the entry space of the blade, or may be rotated clockwise to press down to apply the pressing force to the blade. In addition, the height positions of the upper standing arm 112 and the lower standing arm 114 can be locked through the first locking assembly 116, and the rotation angle of the pressing arm 111 relative to the upper standing arm 112 can be locked through the second locking assembly 118, so that the clamping state between the blade clamp 100 and the blade is maintained, the blade clamp is prevented from loosening after clamping the blade, and the clamping reliability is ensured.

Referring to fig. 4 to 6, in an embodiment, the upper and lower standing

arms

112 and 114 may be a cylindrical hollow structure, i.e., a hollow cylinder, and formed in a nested structure with each other, as shown, may be formed in a rectangular hollow structure. Specifically, the lower part of the upper standing arm 112 is nested inside the upper part of the lower standing arm 114, and can slide relatively along the height direction (Y direction shown in fig. 5) under the pushing of the nip adjusting unit 115, so as to adjust the height/length of the telescopic standing arm composed of the upper standing arm 112 and the lower standing arm 114, thereby improving the use versatility of the blade hoisting tool. For example, when the number of portions in which the upper and

lower arms

112 and 114 are fitted to each other is increased, that is, the height/length of the telescopic arm becomes smaller, the distance between the pressing arm 111 and the holder arm 113 becomes smaller, and the opening degree of the nip becomes smaller; conversely, when the portion where the upper and lower stand

arms

112 and 114 are nested with each other is reduced, the overall height/length of the telescopic stand arm becomes large, the distance between the pressing arm 111 and the retainer arm 113 becomes large, and the degree of opening of the nip becomes large. Alternatively, the upper and lower stand

arms

112 and 114 may be formed of a stainless steel plate to improve strength and prevent corrosion, but the present disclosure is not limited thereto. The present embodiment does not limit the connection manner and the specific shape of the upper standing arm 112 and the lower standing arm 114, as long as the upper standing arm 112 and the lower standing arm 114 can move up and down in the vertical direction (Y direction) to adjust the distance between the pressing arm 111 and the holding arm 113.

The nip adjusting unit 115 may include a pitch extension driving mechanism provided inside the lower stand arm 114. The distance telescopic driving mechanism can adopt a driving mechanism with large thrust and large stroke to adjust the clamping range of the blade in a large range, namely, adjust the size of the clamping opening. The pitch telescoping drive mechanism may be a telescoping cylinder, for example, an automatically controlled hydraulic cylinder. One end of the telescopic cylinder is connected to the lower vertical arm 114, and the other end is connected to the upper vertical arm 112. The telescopic stroke of the telescopic cylinder may be relatively large, and the upper vertical arm 112 is driven to move relative to the lower vertical arm 114 by the linear telescopic motion of the telescopic cylinder, so as to adjust the distance between the pressing arm 111 and the supporting arm 113, but the present disclosure is not limited thereto, and the nip adjusting unit 115 may also be another driving element that can drive the upper vertical arm 112 and the lower vertical arm 114 to move relative to each other, so as to adjust the distance between the pressing arm 111 and the supporting arm 113, and realize the linear telescopic driving, for example, an air cylinder, an electric screw rod, or a bolt with a nut.

The opening and closing degree of the nip can be adjusted by the nip adjusting unit 115 in cooperation with the lifting of the upper standing arm 112 relative to the lower standing arm 114.

After the opening and closing degree of the clamping opening is properly adjusted, in order to maintain the size of the clamping opening to clamp the blade more firmly, a backup first locking assembly 116 is provided on the basis of the lifting function, as shown in fig. 4 to 7, the first locking assembly 116 includes a first locking piece 1161, a second locking piece 1162 and a first driving member 1163.

Wherein the first locking member 1161 is mounted on one of the lower and

upper stand arms

114 and 112. The second locking member 1162 is mounted on the other one of the lower and upper

vertical arms

114 and 112 to be horizontally opposed to the first locking member 1161, and has a locking position and an unlocking position. In the locked position, the second locking member 1162 is engaged with the first locking member 1161 to lock the relative positions of the upper clamping assembly 140 and the lower clamping assembly 150. In the unlocked position, the second lock 1162 is disengaged from the first lock 1161, and the upper stand arm 112 can move relative to the lower stand arm 114. The first drive member 1163 may be a telescoping drive member, such as a hydraulic ram, air cylinder, or lead screw. In the example shown in the drawings, the first driving member 1163 is a cylinder or an air cylinder, a cylinder portion of the first driving member 1163 is installed at a lower portion of the upper upright arm 112, and a piston rod of the first driving member 1163 is connected to the second locking member 1162 for driving the second locking member 1162 to move to at least one of the locking position and the unlocking position.

In the present embodiment, the first locking member 1161 is a long rack gear, and is mounted on the lower stand arm 114 and extends in the direction in which the upper stand arm 112 moves relative to the lower stand arm 114 (Y direction shown in fig. 7). The second locking piece 1162 is a short rack, is installed to be opposed to the long rack, and is movable in a direction (X direction shown in fig. 7) perpendicular to a direction in which the upper stand arm 112 moves relative to the lower stand arm 114 by the driving of the first driving member 1163, so that the short rack and the long rack are engaged with each other when in the locking position. In this embodiment, stepless locking between the upper standing arm 112 and the lower standing arm 114 can be achieved by adopting the engagement of the long rack and the short rack. The length of the long rack may match the telescopic stroke of first drive member 1163, or the relative movement distance between upper clamp assembly 140 and lower clamp assembly 150. The length of the short rack may be smaller than that of the long rack, and the specific length is not limited as long as it has strength capable of locking the upper and lower standing

arms

112 and 114 to each other.

Here, the first driving member 1163 may be a telescopic cylinder installed on the upper standing arm 112, and the short rack is disposed at a first end (i.e., an extended end of the piston rod) of the telescopic cylinder, but the present disclosure is not limited thereto, and the first driving member 1163 may also be other driving elements capable of driving the second locking member 1162 to move in a direction to approach or move away from the first locking member 1161.

Fig. 7 shows that the first locking piece 1161 is formed on the inner side surface of the lower vertical arm 114, the first driving member 1163 is mounted on the upper vertical arm 112, and the second locking piece 1162 is mounted on the telescopic end of the first driving member 1163, but the positions of the first locking piece 1161 and the second locking piece 1162 may be interchanged as necessary.

In the present embodiment, the relative position between the upper standing arm 112 and the lower standing arm 114 is locked by the engagement of the long rack and the short rack with each other, but the present disclosure is not limited thereto, and the first locking member 1161 and the second locking member 1162 may also adopt other locking structures known in the art, for example, a locking hole is engaged with a locking pin, etc., as long as the locking or releasing of the upper standing arm 112 and the lower standing arm 114 can be achieved by the engagement of the first locking member 1161 and the second locking member 1162 with each other.

In the above, the upper vertical arm 112 is moved relative to the lower vertical arm 114 by the nip adjusting unit 115, and the size of the nip is adjusted in a wide range in the vertical direction.

To further adjust the tightness of the clamping blade, the pressing arm 111 may be driven to rotate relative to the standing arm 112 by the angle adjusting unit 117 to adjust the open and close state of the clamping opening of the blade.

Referring to fig. 4 to 6, the blade holding unit 110 according to an embodiment of the present disclosure may further include an angle adjusting unit 117 and a second locking assembly 118. The angle adjusting unit 117 is used to adjust the pivoting angle of the pressing arm 111 with respect to the upper standing arm 112 to adjust the inclination angle of the pressing arm 111 with respect to the upper standing arm 112. The second locking assembly 118 is used to lock the pressing arm 111 with respect to the standing arm 112, so that the safety of the blade holding unit 110 may be improved.

Specifically, the upper portion of the upper standing arm 112 is provided with a pivot shaft 1121, and the pressing arm 111 is connected to the upper standing arm 112 through the pivot shaft 1121. The angle adjusting unit 117 may include a second telescopic driving mechanism, which may be a second telescopic cylinder, a first end of which is hinged to a lower portion of the upper standing arm 112, and a second end of which is hinged to an end of the pressing arm 111, so as to drive the pressing arm 111 to pivot about the pivot shaft 1121 relative to the upper standing arm 112, and adjust an inclination angle of the pressing arm 111 relative to the upper standing arm 112, so as to drive the pressing arm 111 to rotate relative to the upper standing arm 112 through the angle adjusting unit 117, so as to further adjust the magnitude of the clamping force for clamping the blade.

Specifically, the upper portion of the upper standing arm 112 is provided with a pivot shaft 1121 (shown in fig. 5 and 6), and the pressing arm 111 is connected to the upper standing arm 112 through the pivot shaft 1121. A first end of the second telescopic cylinder may be hinged to a lower portion of the upper standing arm 112, and a second end of the second telescopic cylinder may be hinged to an end of the pressing arm 111, thereby driving the pressing arm 111 to pivot about the pivot shaft 1121 with respect to the upper standing arm 112.

Similar to the first telescopic cylinder, the second telescopic cylinder may be an automatically controlled hydraulic cylinder. The second telescopic oil cylinder can adopt the same structural design as the first telescopic oil cylinder and also can adopt different structural designs, namely one of the second telescopic oil cylinder adopts a large-thrust large-stroke design, and the other one adopts a high-precision small-stroke design, so as to meet the control requirements on different precisions and strokes. In addition, the angle adjusting unit 117 may be other driving elements capable of driving the pressing arm 111 to rotate around the pivot shaft 1121 relative to the upper standing arm 112, such as an air cylinder, an electric screw, a bolt with a nut, or the like, in addition to the hydraulic cylinder.

A mounting plate 1122 may be connected to an upper end of the upper stand arm 112, the mounting plate 1122 extending laterally with respect to the upper end of the upper stand arm 112, and the pivot shaft 1121 may be mounted at an end of the mounting plate 1122 so as to be spaced apart from an upper end of the angle adjusting unit 117. The position where the pressing arm 111 is connected to the pivot shaft 1121 is spaced from the end of the pressing arm 111, so that after the end of the pressing arm 111 is connected to the upper end of the angle adjusting unit 117, the pivot shaft 1121 is used as a rotation support shaft, so that the pressing arm 111 can pivot around the pivot shaft 1121 under the driving of the angle adjusting unit 117, thereby adjusting the inclination angle of the pressing arm 111 and accordingly adjusting the clamping force on the blade.

After the angle adjusting unit 117 drives the pressing arm 111 to rotate to a desired angle with respect to the standing arm 112, the rotational positions of the pressing arm 111 and the standing arm 112 may be locked by the second locking assembly 118, thereby maintaining the clamped state between the blade clamp and the blade.

Specifically, the second locking assembly 118 may include a stopper for restricting the first end of the second telescopic cylinder from being retracted, thereby preventing the pressing arm 111 from being pivoted upward to be opened in a state of clamping the vane, resulting in the falling of the vane.

In an embodiment, the stop may be a locking wedge 1181. The locking wedge 1181 has a locking position and an unlocking position, and when the locking position is reached, the locking wedge 1181 abuts against the first end of the second telescopic cylinder to limit the retraction of the second telescopic cylinder; in the unlocked position, locking wedge 1181 disengages from the first end of the second telescopic cylinder, thereby releasing the first end of the second telescopic cylinder so that it can retract.

To enable the locking wedge 1181 to be switched between its locked and unlocked positions, the second locking assembly 118 may further include a second drive member 1182 and a support bracket 1183, and the second drive member 1182 may be a telescopic cylinder to push the locking wedge 1181 to move between the locked and unlocked positions. The cylinder of the second drive member 1182 is mounted on a support bracket 1183, and the piston rod of the second drive member 1182 is connected to the locking wedge 1181 for driving the locking wedge 1181 to move to at least one of its locked and unlocked positions.

The second locking assembly 118 may also include a support bracket 1183. A support 1183 is installed at the upper portion of the upper arm 112, and a locking wedge 1181 is installed on the support 1183 and can move in a direction approaching to or departing from the first end of the second telescopic cylinder. A groove 1184 may be formed on the supporting frame 1183, the groove 1184 extends along the telescopic stroke of the first end of the second telescopic cylinder to guide the movement track of the first end of the second telescopic cylinder, and after the first end of the second telescopic cylinder retracts, the bottom of the groove 1184 supports the first end.

Alternatively, the locking wedge 1181 may have a slope 1181a, and when in the locking position, the slope of the locking wedge 1181 abuts against a lower portion of the first end of the second telescopic cylinder in a direction in which the first end of the second telescopic cylinder retracts, so as to limit the retraction of the first end of the second telescopic cylinder. Through the inclined plane design, when the locking wedge 1181 is pressed by reverse acting force, a friction angle self-locking state is formed due to inclined plane support with an inclined angle, so that after the blade is clamped in place and the second driving member 1182 pushes the locking wedge 1181 to a locking position, the second driving member 1182 can lock the telescopic state of the angle adjusting unit 117 without providing thrust, and a rotating angle between the pressing arm 111 and the upper standing arm 112 is kept, so that the blade is safely clamped without risk.

Fig. 8 to 10 show a process in which the angle adjustment unit 117 drives the pressing arm 111 to rotate relative to the standing arm 112 and is locked by the locking wedge 1181. As shown in fig. 8, the pressing arm 111 is in a state of being rotated outward with respect to the upper standing arm 112, and at this time, the first end of the second telescopic cylinder is in a retracted state; as shown in fig. 9, the first end of the second telescopic cylinder extends out and moves upwards along the groove 1184 of the support 1183, so as to drive the pressing arm 111 to rotate downwards relative to the upper standing arm 112; as shown in fig. 10, after the pressing arm 111 is rotated to a position relative to the upper standing arm 112 to form a clamping opening to clamp the blade, the second driving member 1182 pushes the locking wedge 1181 to move leftward to a locking position, that is, the locking wedge 1181 is embedded between the first end of the second telescopic cylinder and the supporting frame 1183, and the inclined surface of the locking wedge 1181 abuts against the lower portion of the first end of the second telescopic cylinder, so as to limit the retraction of the first end of the second telescopic cylinder. Meanwhile, if the blade is mounted, the second driving member 1182 drives the locking wedge 1181 to move rightwards to the unlocking position, at this time, the first end of the second telescopic cylinder can be freely telescopic, so that the clamping opening is loosened, the blade can be released, and the blade can be safely detached.

The end of the piston rod of the second telescopic cylinder may be provided with a projection to enable the end of the piston rod to interfere with the locking wedge 1181 when the locking wedge 1181 is located between the first end of the telescopic cylinder of the pitch telescopic drive mechanism and the support shelf 1183, thereby preventing retraction of the piston rod.

The present disclosure is not so limited and in another embodiment, as shown in fig. 11, the stop may include a stop 1185 and an eccentric 1186. A barrier 1185 is mounted on the upper vertical arm 112 and is disposed on the telescopic path of the piston rod of the second telescopic cylinder, for example, on the inner side surface of the upper vertical arm 112. The eccentric wheel 1186 is mounted at the end of the piston rod of the second telescopic cylinder and can rotate to a locking position and an unlocking position, and in the locking position of the eccentric wheel 1186, the eccentric wheel 1186 abuts against the baffle 1185, so that the piston rod of the second telescopic cylinder is limited to stretch; in the unlocked position of the eccentric wheel 1186, the eccentric wheel 1186 is disengaged from the baffle 1185, so that the first end of the second telescopic cylinder can be telescopic. The eccentric wheel 1186 may be a disk, and includes a long diameter end and a short diameter end, and a predetermined gap is provided between the baffle 1185 and the piston rod of the second telescopic cylinder, and the predetermined gap is greater than the end diameter of the eccentric wheel 1186 and smaller than the long diameter of the eccentric wheel 1186. In the locking position, the long diameter end rotates to the position of the baffle 1185 and abuts against the baffle 1185, the piston rod of the second telescopic cylinder is prevented from retracting, in the unlocking position, the short diameter end rotates to the position of the baffle 1185 and is separated from the baffle 1185, and the piston rod can freely stretch and retract to pass through the baffle 1185.

Likewise, to allow the eccentric 1186 to be switched between its locked and unlocked positions, the second locking assembly 118 may further include a third drive member 1187, which may be a telescopic drive member, such as a hydraulic ram, an air cylinder, or a lead screw. In the example shown in the figures, the third drive member 1187 may be a telescopic cylinder, the cylinder of the third drive member 1187 may be mounted on the hold-down arm 111, and the piston rod of the third drive member 1187 is hinged to the eccentric 1186 for driving the eccentric 1186 to rotate between the locked and unlocked positions.

Specific structures of the nip adjusting unit 115, the angle adjusting unit 117, the first locking member 116, and the second locking member 118 for adjusting and locking the opening and closing degree of the nip have been described above with reference to the drawings.

Further, the upper clamping assembly 140 and the lower clamping assembly 150 in this embodiment are respectively provided with an upper limiting block 1142 and a lower limiting block 1141 for checking after the blade is mounted in place, so that the blade is mounted and attached in place, one end of the upper limiting block 1142 may be fixedly connected to the upper standing arm 112, and the other end of the upper limiting block 1142 may be provided with a flexible gasket to flexibly contact with the surface of the blade, so as to prevent the blade from being scratched. One end of the lower limiting block 1141 may be fixedly connected to the lower standing arm 114, and the other end of the lower limiting block 1141 may also be provided with a flexible gasket. Preferably, the upper limit block 1142 may be disposed at a corner of the upper clamp assembly 140 formed by the upper standing arm 112 and the pressing arm 111, and the lower limit block 1141 may be disposed at a corner of the lower clamp assembly 150 formed by the lower standing arm 114 and the supporting arm 113.

FIG. 12 illustrates a schematic view of a blade clamp according to an exemplary embodiment of the present disclosure. FIG. 13 shows a schematic view of the blade clamp of FIG. 12 in a state before it is used for pitching a blade. FIG. 14 illustrates a schematic view of the blade clamp of FIG. 12 after being used to pitch a blade.

Referring to fig. 12-14, the blade clamp 100 may further include a pitch drive member 141 that drives the

blade clamping units

110 and 130 to rotate relative to the spar 120; a rail 142 formed on one of the

blade clamping units

110 and 130 and the girder 120; and a rail groove 143 formed on the other one of the

blade clamping units

110 and 130 and the girder 120 and movable with respect to the rail 142.

According to the blade clamp disclosed by the exemplary embodiment of the disclosure, the blade can be subjected to small-range pitch variation in the assembling process and the blade hoisting process of the wind generating set, so that the blade is aligned with the hub and accurately connected to the hub, and in the pitch variation process, the

blade clamping units

110 and 130 can stably rotate relative to the main beam 120 through the matching of the guide rail 142 and the rail groove 143, so that the safety and stability of the blade clamp 100 with the blade in the pitch variation process are ensured. For example, but not limited to, the blade hoisting tool provided by the embodiment can change the pitch within the angle range of-10 ° - +10 °.

Specifically, the pitch driving member 141 is a linear telescopic driving mechanism, one end of the pitch driving member 141 is hinged to the lower portion of the lower standing arm 114, and the other end is hinged to the end of the main beam 120, and the

blade clamping units

110 and 130 are driven to rotate relative to the main beam 120 through the linear telescopic driving of the pitch driving member 141. The linear telescopic driving mechanism is a hydraulic cylinder, the cylinder body of which is arranged on the main beam 120, and the end of the piston rod of the hydraulic cylinder is connected to the lower vertical arm 114. The main beam 120 has a receiving space at both ends thereof for receiving a hydraulic cylinder, the end of a piston rod of the hydraulic cylinder is connected to the lower upright arm 114 through a connecting column perpendicular to the lower upright arm 114, and an opening groove 146 for preventing the connecting column from interfering with the pitch drive member 141 is formed on the lower portion of both ends of the main beam 120. The opening groove 146 is an opening extending in the telescoping direction of the pitch drive member 141. A guide rail 142 is also formed on the other side surface of the lower stand arm 114 opposite to the side surface.

With continued reference to fig. 4 to 6 and 11 to 14, each of the upper clamping assembly 140 and the lower clamping assembly 150 may include a conformal pressing member 119 and a pressing member driving unit 1131 for pushing the conformal pressing member 119 to move along the extending direction of the pressing arm 111 or the supporting arm 113, and the pressing member driving unit 1131 may include a cylinder and a piston rod, specifically, a free end of the piston rod may be hinged to the conformal pressing member 119, and a free end of the cylinder may be hinged to the pressing arm 111 or the supporting arm 113, so as to drive the conformal pressing member 119 to move by the expansion and contraction of the piston rod relative to the cylinder, so that the conformal pressing member 119 is located at a position closely attached to the vane, that is, by adjusting the attaching degree of the vane and the conformal pressing member 119, the vane clamping is more stable, thereby improving the safety during the vane installation process. The extending and retracting direction of the pressing member driving unit 1131 is parallel to the extending direction of the pressing arm 111 or the holding arm 113. Further, the pressing member driving unit 1131 is sleeved in the inner cavity of the pressing arm 111 or the supporting arm 113, so that the overall structure of the blade clamping unit is beautiful.

The conformal compression member 119 may be formed of a member having a shape or an angle adjusted according to an external force, so as to be conformable to the size of the blade and the airfoil shape to the surface of the blade when clamping the blade. The follower compression element 119 in the upper clamp assembly and the follower compression element 119 in the lower clamp assembly are similar in construction and face each other. Hereinafter, the following pressing member 119 in the above clamping assembly is taken as an example, and the structure and the connection relationship with other components will be described in detail.

Referring to fig. 5 and 6, the conformal compression element 119 is rotatable about a first axis 1191 and a second axis 1192, the first axis 1191 extending along the length of the blade and the second axis 1192 extending along the chord length of the blade. The chord length direction of the blade is perpendicular to the length direction of the blade and can be from the front edge to the rear edge of the blade. In other words, the chordwise direction of the blade coincides with the extending direction of the pressing arm 111.

Follower clamp 119 of the upper clamp assembly may include a deflection support 1193 and a clamp block 1194. One side of the deflection support 1193 is rotatably connected to the pressing arm 111 via a first deflection shaft 1191; the clamping block 1194 is rotatably connected with the other side of the deflection support 1193 through a second deflection shaft 1192, so that the clamping block 1194 and the blade are ensured to be fitted in the transverse direction and the longitudinal direction in the process of clamping the blade by the clamping block 1194, and the different profile changes of the blade can be self-adapted along with the shape pressing piece 119.

The specific construction of the compliant clamp 119 of the lower clamp assembly is the same as the compliant clamp 119 of the upper clamp assembly, except that the deflection support 1193 of the compliant clamp 119 of the lower clamp assembly is rotatably connected to the bolster arm 113 and the clamp blocks 1194 of the compliant clamp 119 of the upper and lower clamp assemblies face each other.

Optionally, the conformal compaction member 119 can further include a yaw frame 1195 and a displacement screw 1196. The yaw frame 1195 is connected to the displacement screw 1196 and is capable of moving back and forth (left and right directions in fig. 5 and 7) in the chord length direction of the blade (X direction shown in fig. 5 and 7) by the urging of the displacement screw 1196, thereby adjusting the position of the follower pressing member 119 in the extending direction of the pressing arm 111. The first yaw axis 1191 may be mounted on a yaw frame 1195. After confirming the blade shape each time of installation, the displacement screw 1196 is manually adjusted through the ground, so that the radial deviation caused by the gravity centers of different blade shapes can be adapted.

Optionally, the surfaces of the contact portions of the clamp blocks 1194 with the blade may be coated with a layer of rubber, nylon blocks, or the like, for example, to prevent damage to the blade, increase damping capacity, and reduce wear on the blade when the clamping process is concluded in a collision with the blade.

The blade hoisting tool provided by the disclosure does not need to use an additional turning tool, can avoid risks brought when the blade is installed by using the turning tool and a horizontal blade hoisting tool under the condition that the blade is larger and larger, reduces the development cost of the blade hoisting tool, and is simple in installation process and few in interface.

As shown in fig. 1, the blade hoisting tool further includes a boom 210, a hoisting point connecting beam 220, and a telescopic member 300.

The hanging point connecting cross member 220 may be disposed on the support frame 410 in a horizontal direction, and a guide rail may be formed on the hanging point connecting cross member 220. A first end of the boom 210 may be used to be connected with a hook of a lifting apparatus, and a second end of the boom 210 may be combined with a lifting point connection beam 220 and be movable along a rail, thereby adjusting a position of the lifting point. The first end of the telescopic member 300 may be connected to the support frame 410 and the second end of the telescopic member 300 is connected to the second end of the boom 210 to move the second end of the boom 210 along the rail by the telescopic movement of the telescopic member 300.

In addition, the support frame 410 may be provided therein with a power source (such as a pump station) for powering the telescopic member 300, and the like, in addition to the driving assembly. Optionally, a counterweight (not shown) may be further disposed on the support frame 410 as required, and the posture of the to-be-hung object during hoisting may be further adjusted by disposing a configuration block. Therefore, the double functions of the balancing weight and the lifting point adjustment can facilitate the lifting piece to reach the expected posture during lifting.

In the description of the present application, it is to be understood that the terms "center", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", and the like indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience in describing the present application and simplifying the description, but do not indicate or imply that the referred device or element must have a particular orientation, be constructed in a particular orientation, and be operated, and thus should not be construed as limiting the present application.

The terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present disclosure, "a plurality" means two or more unless otherwise specified.

In the description of the present application, it is to be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meaning of the above terms in the present disclosure can be understood in specific instances by those of ordinary skill in the art.

The described features, structures, or characteristics of the disclosure may be combined in any suitable manner in one or more embodiments. In the above description, numerous specific details are provided to give a thorough understanding of embodiments of the disclosure. One skilled in the relevant art will recognize, however, that the subject matter of the present disclosure can be practiced without one or more of the specific details, or with other methods, components, materials, and so forth. In other instances, well-known structures, materials, or operations are not shown or described in detail to avoid obscuring aspects of the disclosure.

Claims

1. A pitch rotation mechanism, comprising:

a support frame (410) for supporting the frame,

drive unit, drive unit is including rotationally set up in ring gear (610) on braced frame (410), be located driving gear (620) of ring gear (610) inboard and arrange in driving gear (620) periphery with driven gear (630) between the inner periphery of ring gear (610), driven gear (630) can respectively with ring gear (610) with driving gear (620) meshing, with the rotatory drive power transmission of driving gear (620) gives ring gear (610), ring gear (610) are used for fixed connection to blade anchor clamps (100), in order to drive blade anchor clamps (100) along with ring gear (610) are rotatory.

2. The pitch rotation mechanism according to claim 1, wherein the driven gear (630) is provided in plurality, and the plurality of driven gears (630) are arranged on the outer periphery of the driving gear (620) at equal angular intervals.

3. Pitch and rotation mechanism according to claim 2, wherein the gear ring (610) is provided with a plurality of fastener mounting holes (611) so that the gear ring (610) can be fixedly connected to the blade clamp (100) by means of fasteners.

4. A pitch and rotation mechanism according to claim 1, wherein the number of driven gears (630) is 2-6, and is arranged symmetrically around the circumference of the driving gear (620).

5. A blade hoisting tool, characterized in that the blade hoisting tool comprises the pitch rotating mechanism and the blade clamp (100) according to any one of claims 1 to 4, the blade clamp (100) comprises a main beam (120) and blade clamping units (110, 130) arranged at two ends of the main beam (120), and the pitch rotating mechanism is connected to the main beam (120) and can drive the main beam (120) to rotate along with the gear ring (610).

6. The blade hoisting tool according to claim 5, wherein the blade clamping unit (110, 130) comprises an upper clamping assembly (140), a lower clamping assembly (150) and a clamping opening adjusting unit (115), the clamping opening adjusting unit (115) comprises a first telescopic cylinder, and the clamping opening adjusting unit (115) is connected between the upper clamping assembly (140) and the lower clamping assembly (150) and used for adjusting the size of a clamping opening formed by the upper clamping assembly (140) and the lower clamping assembly (150).

7. The blade hoisting tool according to claim 6, wherein the upper clamping assembly (140) comprises a pressing arm (111), an upper standing arm (112) and a first locking assembly (116), the upper standing arm (112) extends downwards from one end of the pressing arm (111), the lower clamping assembly (150) comprises a bearing arm (113) and a lower standing arm (114) extending upwards from one end of the bearing arm (113), and the lower standing arm (114) is connected with the upper standing arm (112) so that the upper clamping assembly (140) and the lower clamping assembly (150) form a space for clamping a blade; the first locking assembly (116) is for locking the upper arm (112) relative to the lower arm (114).

8. The blade lifting tool according to claim 7, wherein the first locking component (116) comprises:

a first locking member (1161) mounted on one of the lower stand arm (114) and the upper stand arm (112);

a second locking member (1162) mounted on the other one of the lower vertical arm (114) and the upper vertical arm (112) and opposite to the first locking member (1161), having a locking position in which the second locking member (1162) is engaged with the first locking member (1161) to lock the relative positions of the upper clamp assembly (140) and the lower clamp assembly (150), and an unlocking position in which the second locking member (1162) is disengaged from the first locking member (1161) so that the upper vertical arm (112) can move relative to the lower vertical arm (114); and

a first drive member (1163) connected to the second locking member (1162) for driving the second locking member (1162) to move to at least one of the locked position and the unlocked position.

9. Blade lifting tool according to claim 8, characterized in that the first locking member (1161) is a long rack mounted on the lower arm (114) and extending in the direction of movement of the upper arm (112) relative to the lower arm (114); the second locking member (1162) is a short rack gear installed on the upper stand arm (112) to be opposite to the long rack gear and movable in a direction perpendicular to a direction in which the upper stand arm (112) moves with respect to the lower stand arm (114) by the driving of the first driving member (1163) such that the short rack gear and the long rack gear are engaged with each other at the locking position, wherein the first driving member (1163) is a telescopic cylinder and the short rack gear is provided at a first end of the telescopic cylinder.

10. The blade hoisting tool according to claim 7, characterized in that the upper part of the upper vertical arm (112) is provided with a pivot shaft (1121), the pressing arm (111) is connected to the upper vertical arm (112) through the pivot shaft (1121),

the blade holding unit (110) further comprises an angle adjusting unit (117) for driving the pressing arm (111) to rotate relative to the upper standing arm (112) to adjust the inclination angle of the pressing arm (111) relative to the upper standing arm (112),

the angle adjusting unit (117) comprises a second telescopic oil cylinder, a first end of the second telescopic oil cylinder is hinged with the lower part of the upper vertical arm (112) and can be telescopic, and a second end of the second telescopic oil cylinder is hinged with the end part of the pressing arm (111), so that the pressing arm (111) is driven to pivot around the pivot shaft (1121).

11. The blade hoisting tool according to claim 10, wherein the blade clamping unit (110) further comprises a second locking assembly (118) for locking the pressing arm (111) relative to the upper standing arm (112), the second locking assembly (118) comprising a stop for limiting retraction of the first end of the second telescopic cylinder.

12. The blade hoisting tool according to claim 11, wherein the stopper is a locking wedge (1181), the locking wedge (1181) has a locking position and an unlocking position, the locking wedge (1181) has a slope (1181a), in the locking position, the slope of the locking wedge (1181) abuts against a lower portion of the first end of the second telescopic cylinder in a direction in which the first end of the second telescopic cylinder retracts so as to limit the retraction of the first end of the second telescopic cylinder, and in the unlocking position, the locking wedge (1181) is disengaged from the first end of the second telescopic cylinder.

13. The blade lifting tool according to claim 12, wherein the second locking assembly (118) further comprises a second driving member (1182) mounted on the hold-down arm (111) for driving the locking wedge (1181) to move to at least one of the locked position and the unlocked position.

14. The blade hoisting tool according to claim 13, wherein the second locking assembly (118) further comprises a support frame (1183), the support frame (1183) is mounted on an upper portion of the upper vertical arm (112), the locking wedge (1181) is mounted on the support frame (1183) and is capable of moving in a direction close to or away from the first end of the second telescopic cylinder, a groove (1184) is formed in the support frame (1183), the groove (1184) extends along a telescopic stroke of the first end of the second telescopic cylinder to guide a movement track of the first end of the second telescopic cylinder, and a bottom of the groove (1184) supports the first end of the second telescopic cylinder after the first end of the second telescopic cylinder is retracted.

15. The blade hoisting tool of claim 11, wherein the stop portion comprises:

a barrier (1185) mounted on the upper boom (112) and disposed on a telescopic path of the first end of the second telescopic cylinder; and

the eccentric wheel (1186) is mounted on the pressing arm (111) and can rotate to a locking position and an unlocking position relative to the pressing arm (111), in the locking position, the eccentric wheel (1186) abuts against a baffle (1185) so as to limit the extension and retraction of the first end of the second telescopic oil cylinder, and in the unlocking position, the eccentric wheel (1186) is separated from the baffle (1185) so as to enable the first end of the second telescopic oil cylinder to extend and retract.

16. The blade lifting tool according to claim 15, wherein the eccentric wheel (1186) comprises a long diameter end and a short diameter end, the long diameter end rotates to the position of the baffle (1185) and abuts against the baffle (1185) in the locking position, and the short diameter end rotates to the position of the baffle (1185) and is separated from the baffle (1185) in the unlocking position.

17. The blade lifting tool according to claim 16, wherein the second locking assembly (118) further comprises a third driving member (1187) mounted on the hold-down arm (111) for driving the eccentric (1186) to move to at least one of the locked position and the unlocked position.