Brake device, turning tool and wind generating set

Abstract

The embodiment of the invention provides a brake device, a turning tool and a wind generating set. The brake device comprises a brake disc, and a plurality of inserting holes distributed in the circumferential direction are formed in the disc face of the brake disc. And the locking module comprises a support and a locking plug pin, the locking plug pin is movably arranged on the support and distributed opposite to the positions of the multiple insertion holes, and the locking plug pin can stretch out to be inserted into one insertion hole. And the brake disc can be effectively locked, so that the brake disc is stably kept at a stalling position, and the brake effect is good.

Description

Technical Field

[0001] The invention relates to the field of turning gear equipment, and in particular to a braking device, a turning gear tooling and a wind turbine generator set. Background Art

[0002] With the development of large-megawatt offshore units, medium-speed permanent magnet technology has gradually become mainstream. Currently, the developed units are at the 18MW level, with blade lengths exceeding 120 meters. Therefore, blade installation has become a technical bottleneck restricting the development of large-megawatt units, and has put forward higher requirements on the braking effect of the brake device during the turning process.

[0003] The braking effect of the brake device of the medium-speed permanent magnet unit currently developed is poor. As the load increases, the brake disc can easily continue to rotate after braking, posing a safety hazard. Summary of the invention

[0004] Therefore, the purpose of the present invention is to provide a brake device, a turning tool and a wind turbine generator set, so as to at least solve the problem that the current brake device has a poor braking effect and the brake disc is likely to continue to rotate after braking.

[0005] A first aspect of the present invention provides a braking device, which includes: a brake disc, a disc surface of which is provided with a plurality of circumferentially distributed holes; a locking module, which includes a bracket and a locking pin, the locking pin being movably arranged on the bracket and distributed relative to the positions of the plurality of holes, and the locking pin being able to extend out and be inserted into one of the holes.

[0006] The brake device provided in the embodiment of the present invention can lock the brake disc by inserting the locking pin into the insertion hole of the brake disc, thereby effectively limiting the brake disc from continuing to rotate, and achieving a good braking effect.

[0007] A second aspect of the present invention provides a turning tool, comprising a braking device as described in the above embodiment.

[0008] The turning tool provided in the embodiment of this aspect has the braking device of the above-mentioned embodiment, and thus has the beneficial effects of the above-mentioned embodiment, which will not be described in detail here.

[0009] A third aspect of the present invention provides a wind turbine generator set, comprising a brake device or a turning tool as described in the above embodiment.

[0010] The wind turbine generator set provided by the embodiment of this aspect has the brake device or the turning tool of the above embodiment, and thus has the beneficial effects of the above embodiment, which will not be described in detail here.

[0011] Additional aspects and / or advantages of the present general inventive concept will be set forth in part in the following description and in part will be obvious from the description, or may be learned through practice of the present general inventive concept. BRIEF DESCRIPTION OF THE DRAWINGS

[0012] The above and other objects and features of the present invention will become more apparent through the following description of the embodiments in conjunction with the accompanying drawings, in which:

[0013] Figure 1 A schematic diagram of a turning tool with a brake device according to an embodiment of the present application is shown;

[0014] Figure 2 Shows Figure 1 Schematic cross-sectional view along the AA direction;

[0015] Figure 3 A schematic diagram of disassembly of a turning tool with a brake device according to an embodiment of the present application is shown;

[0016] Figure 4 Shows Figure 3 A partial enlarged schematic diagram of the M in the middle;

[0017] Figure 5 A partial disassembled schematic diagram of a brake device according to an embodiment of the present application is shown;

[0018] Figure 6 A schematic structural diagram of a brake disc according to an embodiment of the present application is shown;

[0019] Figure 7 Another schematic structural diagram of a brake disc according to an embodiment of the present application is shown;

[0020] Figure 8 A schematic diagram showing the structure of a locking latch according to an embodiment of the present application is shown;

[0021] Fig. 9 A schematic diagram showing the structure of a locking bolt in a natural state according to an embodiment of the present application is shown;

[0022] Fig.10 A schematic diagram showing the structure of a locking pin in a compression process according to an embodiment of the present application is shown;

[0023] Fig.11 A schematic diagram showing the structure of a locking pin in a compressed state according to an embodiment of the present application is shown;

[0024] Fig.12 A schematic diagram showing the structure of a second transmission gear and a connecting pin in one embodiment of the present application is shown;

[0025] Fig.13A schematic diagram showing the structure of a connecting pin according to an embodiment of the present application is shown;

[0026] Fig.14 A schematic diagram showing the structure of a connecting pin in a natural state according to an embodiment of the present application is shown;

[0027] Fig.15 A schematic diagram showing the structure of a connecting pin in a compression process according to an embodiment of the present application is shown;

[0028] Fig.16 A schematic diagram showing the structure of a connecting pin in a compressed state according to an embodiment of the present application is shown;

[0029] Figures 1 to 16 Description of Figure Numbers:

[0030] 110 brake disc, 111 socket, 1111 big end, 1112 small end, 112 connecting shaft,

[0031] 120 bracket, 121 first baffle, 1211 first avoidance hole, 122 second baffle, 1221 second avoidance hole,

[0032] 130 locking pin, 131 first inner shaft, 132 first outer shaft sheet, 133 first spring,

[0033] 140 brake caliper, 141 through hole,

[0034] 151 first transmission gear,

[0035] 152 second transmission gear,

[0036] 160 connecting pin, 161 second inner shaft, 162 second outer shaft sheet, 1621 spring receiving groove, 163 second spring, 164 non-Newtonian fluid layer,

[0037] 170 support seat, 171 support shaft, 172 shaft sleeve, 173 end flange,

[0038] 181 drive motor, 182 gear box,

[0039] 190 protective cover,

[0040] 211 rotary encoder, 212 laser sensor. DETAILED DESCRIPTION

[0041] The following specific embodiments are provided to help the reader obtain a comprehensive understanding of the methods, devices and / or systems described herein. However, after understanding the disclosure of the present application, various changes, modifications and equivalents of the methods, devices and / or systems described herein will be clear. For example, the order of operations described herein is only an example and is not limited to those orders set forth herein, but can be changed as will be clear after understanding the disclosure of the present application, except for operations that must occur in a specific order. In addition, for greater clarity and simplicity, the description of features known in the art may be omitted.

[0042] The features described herein can be implemented in different forms and should not be construed as being limited to the examples described herein. Rather, the examples described herein have been provided to illustrate only some of the many possible ways to implement the methods, devices, and / or systems described herein, which will be clear after understanding the disclosure of the present application.

[0043] As used herein, the term "and / or" includes any one of the associated listed items and any combination of any two or more.

[0044] Although terms such as "first", "second", and "third" may be used herein to describe various members, components, regions, layers, or portions, these members, components, regions, layers, or portions should not be limited by these terms. Instead, these terms are only used to distinguish one member, component, region, layer, or portion from another member, component, region, layer, or portion. Therefore, without departing from the teachings of the examples described herein, the first member, first component, first region, first layer, or first portion referred to in the examples may also be referred to as the second member, second component, second region, second layer, or second portion.

[0045] In the specification, when an element such as a layer, a region or a substrate is described as being “on”, “connected to” or “coupled to” another element, the element may be directly “on”, “connected to” or “coupled to” another element, or one or more other elements may be present therebetween. Conversely, when an element is described as being “directly on”, “directly connected to” or “directly coupled to” another element, other elements may not be present therebetween.

[0046] The terms used herein are only used to describe various examples and are not intended to limit the disclosure. Unless the context clearly indicates otherwise, the singular form is also intended to include the plural form. The terms "comprise", "include" and "have" indicate the presence of the described features, quantities, operations, components, elements and / or combinations thereof, but do not exclude the presence or addition of one or more other features, quantities, operations, components, elements and / or combinations thereof. The term "plurality" represents any number of two and more than two.

[0047] The definitions of directional terms such as "above", "below", "top" and "bottom" in this application are based on the orientation of the product in normal use, unless otherwise specified.

[0048] Unless otherwise defined, all terms used herein, including technical terms and scientific terms, have the same meaning as those generally understood by ordinary technicians in the field to which the present invention belongs after understanding the present invention. Unless explicitly defined as such herein, terms such as those defined in general dictionaries should be interpreted as having a meaning consistent with their meaning in the context of the relevant field and the present invention, and should not be interpreted in an idealized or overly formal way.

[0049] With the development of large-megawatt offshore units, medium-speed permanent magnet technology has gradually become the mainstream. Currently, the units developed are at the 18MW level, and the blade length exceeds 120 meters. Therefore, blade installation has become a technical bottleneck restricting the development of large-megawatt units. The brake device in the turning tool of the currently developed medium-speed permanent magnet unit is prone to uncontrollable rotation during the blade installation process when the impeller is turned, which poses a great safety risk to the construction and installation. For example, when the internal transmission parts of the turning tool slip or loosen, no-load operation will occur, and the brake disc will rotate too fast and the turning will fail. For example, if the blades are too heavy or the internal transmission parts of the turning tool are stuck, the brake disc may rotate too slowly, and the motor is driven at full power, which is easy to cause a fault. However, the current brake device cannot effectively lock the brake disc after a turning failure occurs, increasing safety hazards.

[0050] Based on this, an embodiment of the present invention proposes a braking device.

[0051] The brake device can be used for the turning tool. During the turning process, the turning component to be turned is driven to rotate by some components of the brake device to perform the turning operation. When the turning needs to be stopped, the brake operation is performed by some components of the brake device to stop the turning. The brake device is used to accurately control the turning tool to stop the turning, thereby improving the turning safety.

[0052] Here, the turning tool can be applied to a wind turbine generator set, so that the brake device therein can be applied to the wind turbine generator set. For example, during the installation of the blades of a wind turbine generator set, the turning tool turns the hub to rotate the blade interface of the hub to a horizontal position or other set position, so that the installer can connect the blade and the hub together. Specifically, the brake device is connected to the rotor of the generator (not shown in the figure), and by driving the rotor to rotate, the hub connected to the rotor is driven to rotate, and when the brake device performs a braking operation, the rotor is driven to stop rotating, and the turning operation is stopped.

[0053] Of course, the brake device may not be used on the turning tool and may not be used during the turning process, but may be used to brake other components that require braking.

[0054] For the convenience of description, the following detailed description is given by taking the braking device applied to a turning tool, connected to the rotor of a generator of a wind turbine generator set, and turning the hub as an example, but the description is not limited thereto.

[0055] like Figure 3 As shown, the brake device includes a brake disc 110 and a locking module. The brake disc 110 is used to connect with the component to be cranked. The brake disc 110 can drive the component to be cranked to rotate. For example, the brake disc 110 can drive the generator rotor to rotate for cranking. The locking module can lock the brake disc 110 to limit the rotation of the brake disc 110.

[0056] Specifically, if Figure 4 , Figure 5 , Figure 6 and Figure 7 As shown, a plurality of circumferentially distributed plug holes 111 are provided on the surface of the brake disc 110. The locking module includes a bracket 120 and a locking pin 130. The locking pin 130 is movably arranged on the bracket 120 and is distributed relative to the positions of the plurality of plug holes 111. The locking pin 130 can extend and be inserted into one of the plug holes 111.

[0057] The locking pin 130 is inserted into the socket 111 to limit the rotation of the brake disc 110. Compared with the related art that only relies on the motor to stop to prevent the brake disc 110 from rotating, and the large torque only relies on the motor braking, it is beneficial to effectively stop the turning tool and stably maintain it in the stopped position. Compared with the related art that only relies on the hydraulic drive brake caliper 140 to control the brake disc 110 to stop, the problem of load stall caused by the risk of leakage can be avoided. The structure of the turning tool itself and the components to be turned can be protected to avoid continued rotation after a fault occurs and expand the impact of the fault. In addition, it is convenient for the crew to install, repair and other operations on the unit and the turning tool after the brake disc 110 stops stably, which can improve the safety of the unit installers.

[0058] The locking module further includes a locking pin driver (not shown in the figure), which is used to push the locking pin 130 into the insertion hole 111 and drive the locking pin 130 to move out of the insertion hole 111. Here, the locking pin driver can be an electric driver, such as an electromagnetic push rod, etc., to avoid leakage caused by hydraulic drive, and has high reliability. Of course, the locking pin driver can also be a hydraulic driver.

[0059] In addition, the braking device also includes a brake disc driver for driving the brake disc 110 to rotate. The locking pin driver and the brake disc driver can be independent of each other, independently driving the locking pin 130 to extend and lock, and independently stopping the driving of the brake disc 110 to rotate, thereby being able to perform multiple braking operations on the brake disc 110.

[0060] Furthermore, the locking pin 130 can contract and expand radially. Compared with a rigid structure, the locking pin 130 can buffer the impact force with the inner wall of the insertion hole 111 of the brake disc 110, thereby reducing the probability of the locking pin 130 breaking.

[0061] Regarding the specific structure of the locking pin 130, in some embodiments, as Figure 8 , Fig. 9 , Fig.10 and Fig.11 As shown, the locking latch 130 includes a first inner shaft 131, a plurality of first outer shaft pieces 132, and a first elastic component. The plurality of first outer shaft pieces 132 are circumferentially distributed on the outside of the first inner shaft 131 to surround the first inner shaft 131. The first elastic component connects the first inner shaft 131 and the plurality of first outer shaft pieces 132. The plurality of first outer shaft pieces 132 can be compressed and contracted to abut against each other in the circumferential direction of the first inner shaft 131 and press the first elastic component inwardly. The plurality of first outer shaft pieces 132 can also expand outward and separate from each other under the elastic force of the first elastic component.

[0062] This structure, which has a first inner shaft 131 inside and a plurality of first outer shaft sheets 132 that can shrink and expand outside, can ensure that the locking pin 130 has a certain structural strength and can achieve expansion and contraction, so as to stably support the rotor. Moreover, since the outer peripheral part is designed as a slice body, the production cost is low, and it can be made of waste scraps to reduce costs. In addition, the outer periphery of the locking pin 130 adopts a sheet body design, which is used to lock the brake disc 110 in the contracted state and is used for buffering inside the socket 111 of the brake disc 110 in the expanded state, which can ensure that the mechanical structure will not be subjected to unbearable impact loads during instantaneous braking. The shrinkable and expandable locking pin 130 can play a buffering role during installation and load-carrying rotation.

[0063] Figure 8 A side view of the locking bolt 130 is shown. Fig. 9 , Fig.10 and Fig.11 They are Figure 8 The cross-sectional view is taken along the PP direction, and is a cross-sectional view of the locking pin 130 in different states. Fig. 9 A cross-sectional view of the locking pin 130 in a natural state without being squeezed is shown. It can be seen that when the locking pin 130 is not squeezed, the cross-section is substantially a perfect circle. Fig.10 The schematic diagram shows the locking pin 130 in the process of being compressed. At this time, the first elastic component is compressed, and two adjacent first outer shaft sheets 132 have not yet completely abutted against each other. Fig.11 The cross-sectional schematic diagram of the locking pin 130 in a compressed state is shown. At this time, any two circumferentially adjacent first outer shaft pieces 132 abut against each other, and the locking pin 130 is compressed to a minimum state.

[0064] Here, the plurality of first outer shaft pieces 132 can be designed according to the maximum diameter, that is, when the locking pin 130 is observed along the axial direction of the locking pin 130, the connecting line of the outer contours of the plurality of first outer shaft pieces 132 in the natural state without compression is a circle. Therefore, after the first outer shaft pieces 132 are squeezed and contracted, the connecting line of the outer contours of the plurality of first outer shaft pieces 132 is non-circular and has a certain bulge, as shown in FIG. Fig.11 The four bulges of the upper, lower, left and right connecting pin 160 are based on the center position in the figure, similar to the square and circle structure. This structure can ensure the buffer after the shaft hole gap deviation is large. Even if the locking pin 130 rotates, it will get stuck due to the non-circular structure after rotating to a certain angle, thereby ensuring that the locking pin 130 can stably withstand the torque. Fig. 9 and Fig.11 As shown, L1 is the lateral movement space of the first outer shaft piece 132, L2 is the minimum diameter of the first outer shaft piece 132 in a compressed state, L3 is the buffer area of ​​the first outer shaft piece 132, and L4 is the difference between the maximum adaptation diameter and the minimum adaptation diameter of the locking pin 130. Therefore, in order to adapt to different brake discs 110, the size of the buffer area can be set according to the above four parameters to ensure that the overall force of the locking pin 130 is uniform and safe and reliable.

[0065] In addition, the number of the plurality of first outer shaft pieces 132 is at least two, including but not limited to three, four, etc. The number of the first outer shaft pieces 132 can be designed according to actual force requirements, and can be symmetrically or asymmetrically distributed relative to the center line of the first inner shaft 131 .

[0066] In addition, the cross-section of the locking pin 130 in the natural state may be in other shapes besides being roughly circular, such as square, polygonal, etc.

[0067] For the specific structure of the first elastic component, further, as Figure 8 , Fig. 9 , Fig.10 and Fig.11 As shown, the first elastic component includes a plurality of first springs 133, which are respectively connected to the outer side of the first inner shaft 131 and the inner side of the first outer shaft piece 132. The first springs 133 are used to support the plurality of first outer shaft pieces 132, so as to facilitate radial compression under pressure. Moreover, since the first springs 133 are located between the first inner shaft 131 and the outer shaft piece, there will be no interference problem between the plurality of first outer shaft pieces 132 during the contraction and expansion process of the locking bolt 130. Moreover, the elastic force of the spring is relatively large, and a relatively large supporting force can be provided to cause the locking bolt 130 to be closely abutted against the insertion hole 111, thereby improving the locking effect and buffering the impact borne by the locking bolt 130.

[0068] The first spring 133 may be a leaf spring, extending along the axial direction of the first inner shaft 131. The leaf spring takes up little space and is easy to install. Of course, the first spring 133 may not be a leaf spring, and multiple structures of this type may be used.

[0069] In addition, one, two or more first springs 133 may be provided between each first outer shaft piece 132 and the first inner shaft 131. The two or more first springs 133 may be spaced apart in the circumferential direction of the first inner shaft 131, or spaced apart in the axial direction of the first inner shaft 131. The compression resistance of the locking pin 130 may be increased, which is conducive to keeping the plurality of first outer shaft pieces 132 in an expanded state, and not prone to local collapse due to failure of the first springs 133.

[0070] Of course, the first spring 133 can also be replaced by other structures, such as a first rubber pad or other damping device that can achieve this function, which is also within the protection scope of the present application. Based on the situation that the first elastic component includes multiple first rubber pads, the first rubber pad can be in a long strip shape, extending along the axial direction of the first inner shaft 131, and at least one first rubber pad is connected between each first outer shaft sheet 132 and the first inner shaft 131 in the circumferential direction of the first inner shaft 131.

[0071] In addition, in other embodiments, the first elastic component includes a plurality of first springs, which are different from the above embodiments in that the first springs are connected between any two circumferentially adjacent first outer shaft pieces 132. The first elastic component also includes a non-Newtonian fluid layer, which is wrapped around the outside of the first inner shaft 131 and can support the plurality of first outer shaft pieces 132 on the inside. Due to the material properties of the non-Newtonian fluid, the greater the torque, the greater the reaction force, and it is strong when it meets rigidity, and it has a buffering effect while ensuring a braking effect.

[0072] Furthermore, the locking pin 130 is in a tapered structure with one end being large and the other end being small. The cross-sectional area of ​​the end of the locking pin 130 facing the brake disc 110 is smaller than the cross-sectional area of ​​the end away from the brake disc 110. This facilitates the insertion of the locking pin 130 into the insertion hole 111 and helps ensure that the locking pin 130 abuts against the insertion hole 111. Here, the first inner shaft 131 and the plurality of first outer shaft pieces 132 may both be in a tapered structure, or the first inner shaft 131 may be in a straight cylindrical shape, and the plurality of first outer shaft pieces 132 may be distributed roughly in a tapered shape.

[0073] As for the specific structure of the insertion hole 111, the insertion hole 111 is further configured as a long strip hole extending along the circumference of the brake disc 110. On the one hand, the probability of the locking pin 130 being inserted into the insertion hole 111 is increased, and it is convenient for the locking pin 130 to lock the brake disc 110. On the other hand, after the locking pin 130 is inserted into one end of the insertion hole 111, as the brake disc 110 rotates, the locking pin 130 can move a certain distance in the insertion hole 111 and then abut against the inner wall of the insertion hole 111, which has a certain buffering effect compared with locking immediately after being inserted into the insertion hole 111.

[0074] Furthermore, if Figure 6 and Figure 7 As shown, the space enclosed by one end of the plug hole 111 in the circumferential direction of the brake disc 110 is large, which is configured as a large head end 1111, and the space enclosed by the other end of the plug hole 111 in the circumferential direction of the brake disc 110 is small, which is configured as a small head end 1112. The locking pin 130 can shrink and expand radially. When the brake disc 110 rotates from the direction of the small head end 1112 of a plug hole 111 to the direction of the large head end 1111, the locking pin 130 can be inserted into the plug hole 111 through the large head end 1111, and then squeezed and shrunk to abut and cooperate with the small head end 1112. When the brake disc 110 rotates from the direction of the large head end 1111 of a plug hole 111 to the direction of the small head end 1112, the locking pin 130 can be inserted into the plug hole 111 and abut and cooperate with the large head end 1111.

[0075] The locking pin 130 can shrink and expand radially, and after being inserted into the socket 111, it is gradually squeezed and shrunk by the small head end 1112 of the socket 111 as the brake disc 110 rotates. Compared with the rigid collision between the locking pin 130 and the socket 111, the impact force can be reduced, and the risk of the locking pin 130 breaking can be reduced, thereby ensuring that the locking pin 130 stably locks the brake disc 110. In addition, during the locking process, the locking capacity can be gradually adjusted as the size of the brake disc 110 hole is adjusted, and a buffer zone is reserved, so that the locking pin 130 will not be subjected to too much impact, ensuring the stability of the mechanical structure. The problem of the concentration of individual pins caused by the uneven force of the traditional pins being too small can be solved.

[0076] In a specific application, during the locking process of the locking pin 130, it first penetrates into the mounting hole on the left side of the brake disc 110, that is, the first avoidance hole 1211 on the bracket 120. At this time, the shaft hole gap is very large and there is a problem of eccentricity. When the locking pin 130 gradually penetrates (pushes toward the right side of the brake disc 110), the first elastic component is gradually compressed and gradually subjected to force. As the brake disc 110 rotates, the position of the locking pin 130 remains fixed, but the diameter is gradually compressed to match the large and small head ends 1112 of the socket 111 of the brake disc 110, thereby realizing damping mechanical control braking. Finally, the locking pin 130 and the socket 111 of the brake disc 110 are seamlessly fitted together for braking, thereby realizing the load braking function.

[0077] During the operation of the turning gear with load, the first outer shaft sheet 132 is gradually compressed, and the reaction force is greater, so there will be no problem of deformation and disengagement of the locking pin 130 due to force. The advantage of this structure is that when installing and disassembling, it is only necessary to slightly reverse the brake disc 110 to move the locking pin 130 toward the large end 1111 of the insertion hole 111, and then the locking pin 130 can be pulled out through the locking pin driving member, which is extremely easy to insert and pull out. Moreover, during the operation of the turning gear with load, the contracted locking pin 130 is roughly in a semi-circular structure, which can well transmit the force, increase the contact area, and have a good locking effect.

[0078] The unit of the related art does not have a brake disc 110, and the traditional brake disc 110 cannot brake quickly. It mainly slows down the rotation speed by friction of the friction plate and cannot stop at a fixed point. However, the present embodiment is designed with a self-locking brake disc 110 structure. Through the large and small head ends 1112 of the insertion hole 111 of the brake disc 110 and the adjustment of the locking pin 130, the brake disc 110 is used to slow down the rotation speed of the loaded turntable. At the same time, through the evenly distributed hole positions of the insertion hole 111, the locking pin 130 is inserted from the large head end 1111, and the locking pin 130 is squeezed by the rotation of the brake disc 110 to achieve buffer locking of the pin. At the same time, the hole position of the brake disc 110 becomes smaller. After the buffer zone ends, it can be accurately positioned and locked to ensure the safe locking of the turntable with load.

[0079] Furthermore, if Figure 6 As shown, the inner end surface of the large end 1111 is a first arcuate surface, which can contact the outer surface of the locking pin 130 in a natural state, and the inner end surface of the small end 1112 is a second arcuate surface, which can contact the outer surface of the locking pin 130 in a contracted state. The locking effect is good.

[0080] As an example, Figure 6 and Figure 7As shown, the large end 1111 and the small end 1112 of the socket 111 are circular, connected by a smooth arc in the middle, similar to a water drop shape, which can achieve a smooth transition from a large diameter to a small diameter of the locking pin 130. Of course, the large end 1111 and the small end 1112 can also be connected by two tangents in the middle to facilitate processing. The diameter of the circle corresponding to the small end 1112 can be the diameter of the locking pin 130 after being compressed, and the diameter of the circle corresponding to the large end 1111 can be the diameter of the locking pin 130 in the expanded state. It is convenient for the locking pin 130 to fully abut against the socket 111 and lock. Or the diameter of the locking pin 130 in the expanded state, that is, its diameter in the natural state is smaller than the diameter of the circle corresponding to the large end 1111, and larger than the diameter of the circle corresponding to the small end 1112, so that the locking pin 130 is smoothly inserted into the socket 111.

[0081] refer to Figure 6 , the distance M between the center of the large circle corresponding to the large end 1111 and the center of the small circle corresponding to the small end 1112, as well as the small circle pitch circle radius R1 and the large circle pitch circle radius R2 can be designed according to the transmission ratio of the unit gearbox 182 and the instantaneous impeller locking time allowed by the impeller end to meet the acceleration impact caused by the sudden impeller load stop of the unit. When the turning gear is running with load, M is the buffer area of ​​the locking pin 130. Therefore, the instantaneous locking of the brake disc 110 can set the pin buffer area according to the above parameters to ensure that the overall force of the locking pin 130 is uniform and safe and reliable. In addition, the number of the sockets 111 on the brake disc 110 can be designed according to the actual requirements of braking accuracy, which is generally greater than 3. The maximum number depends on the load torque, that is, when there are many holes, the structure of the brake disc 110 itself can meet the load requirements. The hole form can be symmetrical, evenly distributed, or set according to the structure of the bracket 120. Therefore, in addition to the above-mentioned shapes, the structure of the socket 111 can also include other structures such as round, square, diamond, etc., which belong to the present design concept.

[0082] As an example, the width of the insertion hole 111 in the radial direction of the brake disc 110 gradually decreases from the large end 1111 to the small end 1112. This facilitates the locking pin 130 to be gradually compressed in the insertion hole 111. The outer diameter of the locking pin 130 in a natural state is smaller than the width of the large end 1111 in the radial direction of the brake disc 110, and larger than the width of the small end 1112 in the radial direction of the brake disc 110.

[0083] Furthermore, if Figure 6As shown, multiple sockets 111 are distributed in multiple circles around the rotation center line of the brake disc 110. In each circle of sockets 111, the large end 1111 of any socket 111 is close to the small end 1112 of the adjacent socket 111. The arrangement directions of the two radially adjacent circles of sockets 111 are opposite, that is, the arrangement directions of the inner and outer circles of sockets 111 are opposite. For example, the large end 1111 of one circle of sockets 111 faces clockwise, and the large end 1111 of the other circle of sockets 111 faces counterclockwise. There are multiple locking pins 130, and each circle of sockets 111 is arranged opposite to at least one locking pin 130. It is achieved that when the brake disc 110 rotates clockwise and counterclockwise, the locking pin 130 can buffer and lock the brake disc 110 without too much impact on the brake disc 110.

[0084] For example, the multiple jacks 111 are distributed in two circles, inner and outer, around the rotation center line of the brake disc 110. Figure 6 , the big end 1111 of each socket 111 of the inner circle is in the counterclockwise direction of its small end 1112, and the big end 1111 of each socket 111 of the outer circle is in the clockwise direction of its small end 1112. There are two locking pins 130, corresponding to the positions of the inner circle socket 111 and the outer circle socket 111 respectively. When the brake disc 110 rotates clockwise, the locking pin 130 corresponding to the outer circle is first inserted into the socket 111 through the big end 1111 of the outer circle socket 111, and then as the brake disc 110 rotates, it is squeezed and contracted by the inner wall of the socket 111 until it abuts against the socket 111, thereby locking the brake disc 110. Meanwhile, when the locking pin 130 corresponding to the inner ring insertion hole 111 is opposite to the small end 1112, it will not extend into the insertion hole 111. As the brake disc 110 rotates, the size of the insertion hole 111 gradually increases, and the locking pin 130 is inserted into the insertion hole 111, and can abut against the large end 1111 of the inner ring insertion hole 111 when the outer ring locking pin 130 abuts against the outer ring insertion hole 111. While achieving double locking of the inner and outer rings, the outer ring locking pin 130 can also buffer and lock the brake disc 110 to avoid a large impact.

[0085] Of course, the number of the locking pins 130 here can be four, six, etc. in addition to two, and each circle of the sockets 111 corresponds to multiple locking pins 130, firmly locking the brake disc 110. Similarly, the sockets 111 can also be distributed in three circles, four circles, or even more circles, corresponding to more locking pins 130, firmly locking the brake disc 110. The structural design of the large and small ends of the sockets 111 can squeeze all the locking pins 130 during the rotation process, so that all the locking pins 130 are more evenly stressed, ensuring that the torque transmission of the mechanical interface is safe and reliable.

[0086] Regarding the specific structure of the bracket 120, further, as Figure 4 , Figure 5 and Figure 6 As shown, the bracket 120 includes a first baffle 121 and a second baffle 122, which are respectively located on both sides of the brake disc 110, a first avoidance hole 1211 is provided on the first baffle 121, and a second avoidance hole 1221 is provided on the second baffle 122, and the insertion hole 111 is a through hole, and the locking pin 130 can pass through the insertion hole 111 through the first avoidance hole 1211 and then be inserted into the second avoidance hole 1221. The locking pin 130 is inserted into the two baffles and the brake disc 110 at the same time, which can effectively limit the brake disc 110 and has a good locking effect.

[0087] Of course, in other examples, the bracket 120 may also include only the first baffle 121 or the second baffle 122, and the insertion hole 111 may be a countersunk hole in addition to a through hole, and the locking pin 130 extends from the avoidance hole on one side of the brake disc 110 into the countersunk hole to lock the brake disc 110. Since the insertion hole 111 is a countersunk hole, it has little effect on the structural strength of the brake disc 110, which is conducive to bearing a larger torque.

[0088] Furthermore, if Figure 4 and Figure 5 As shown, the brake device also includes a brake module, which is arranged outside the brake disc 110 and can perform friction braking on the brake disc 110 .

[0089] In addition to locking the brake disc 110 with the locking pin 130, the brake module can also be used to perform friction braking on the brake disc 110, and the two are redundant protections. When the turning gear has a problem and needs to stop turning gear, the brake can be applied in two ways, and the rotation of the brake disc 110 can be limited in two ways, which can ensure that the turning gear tooling does not rotate by mistake, thereby improving the safety of the crew.

[0090] like Figure 4 and Figure 5 As shown, the brake module includes a brake caliper 140 and a caliper driver (not shown in the figure), and the caliper driver can drive the brake caliper 140 to engage the brake to perform friction braking on the brake disc 110.

[0091] In a specific application, the clamp driving member can be a hydraulic driving member or a motor driving member. The brake clamp 140 is disposed on the bracket 120 , between the first baffle 121 and the second baffle 122 , and on both sides of the brake disc 110 , for clamping the brake disc 110 .

[0092] Regarding the connection between the brake disc 110 and the generator rotor, further, in some embodiments, the brake device further includes a rotatable member. The rotatable member is used to connect with the generator rotor to drive the rotor to rotate, thereby driving the hub linked to the rotor to rotate for turning, which is convenient for installing the blades.

[0093] Specifically, since the blades are heavy, the brake device is under heavy load during loaded operation. To improve the stability of the turning rotation, the brake disc 110 can be driven to rotate the rotatable part through gear transmission, which can bear a large torque and is conducive to stable turning.

[0094] As an example, Figure 1 , Figure 2 and Figure 3 As shown, the brake device further includes a first transmission gear 151 and a second transmission gear 152. The first transmission gear 151 is connected to the brake disc 110 and rotates synchronously with the brake disc 110. The first transmission gear 151 is meshed with the second transmission gear 152. The second transmission gear 152 is configured as a rotatable member.

[0095] Reference here Figure 1 , the number of brake discs 110 can be two, the number of first transmission gears 151 can be two, and the two first transmission gears 151 can mesh with the second transmission gear 152 at the same time, driving the second transmission gear 152 to rotate in two directions, and the rotation stability is good. At this time, reference Figure 3 The brake disc driving member for driving the brake disc 110 to rotate may include two driving motors 181 and two gear boxes 182, namely a first driving motor, a second driving motor, a first gear box and a second gear box. The first driving motor is connected to one brake disc 110 via the first gear box, and the second driving motor is connected to another brake disc 110 via the second gear box.

[0096] Of course, in other examples, the second transmission gear 152 and the rotatable member may be two independent components, which are connected together for synchronous rotation.

[0097] Furthermore, in order to facilitate the connection between the rotatable member and the rotor, a plurality of connecting pins 160 are provided on one side of the rotatable member, and the plurality of connecting pins 160 are used for plugging and connecting with the rotor of the generator. Figure 1 , Figure 2 , Figure 3 and Fig.12 The rotatable part is the second transmission gear 152, and a plurality of connecting pins 160 are arranged on one side of the second transmission gear 152. The structure is simple, the installation is convenient, and it is convenient to drive the rotor to rotate synchronously.

[0098] Furthermore, the plurality of connecting pins 160 can contract and expand in the radial direction.

[0099] In the related art, the method of connecting the turning tooling and the rotor mostly adopts a rigid pin inserted into the plug hole of the rotor. The installation gap between the plug hole and the pin has a large deviation, and the design and manufacturing precision cannot be synchronized. A large installation gap will cause uneven force on the pin, and a small installation gap will cause multiple plug holes to be unable to fully insert the pins. Moreover, the multiple pins of the current turning tooling cannot all be stressed at the same time after installation, and there is an eccentricity problem, which causes individual pins to be stressed and easy to break. Once the pin connected to the generator here breaks, the impeller will rotate uncontrollably. In this embodiment, multiple connecting pins 160 can shrink and expand radially. Multiple connecting pins 160 are inserted into the plug hole of the rotor under pressure, so that multiple connecting pins 160 can be stressed more evenly, and it is not easy for a single connecting pin 160 to break, thereby avoiding safety problems caused by pin breakage.

[0100] Specifically, if Figure 1 , Figure 3 and Fig.12 As shown, a plurality of connecting pins 160 are circumferentially spaced around the rotation centerline of the second transmission gear 152. A plurality of connecting pins 160 are inserted into the plug-in holes of the rotor under pressure. In the process of hoisting the blades, when one or two blades have been hoisted and the brake device is rotating under load, under the influence of load and torque, if the connecting pin 160 is a simple metal shaft with an assembly gap between the connecting pin and the plug-in hole, it is possible that the connecting pin 160 at the top is almost not subjected to force, while the connecting pin 160 at the bottom is subjected to the greatest force. In this embodiment, the plurality of connecting pins 160 are able to contract and expand radially, so that the connecting pins 160 located at various locations can effectively support the rotor, which is conducive to a more balanced overall force on the plurality of connecting pins 160 and avoids breakage.

[0101] Regarding the specific structure of the connecting pin 160, in some embodiments, as Fig.13 , Fig.14 , Fig.15 and Fig.16 As shown, each connecting pin 160 includes a second inner shaft 161, a plurality of second outer shaft pieces 162, and a second elastic component. The plurality of second outer shaft pieces 162 are circumferentially distributed on the outer side of the second inner shaft 161 to surround the second inner shaft 161. The second elastic component connects the second inner shaft 161 and the plurality of second outer shaft pieces 162. The plurality of second outer shaft pieces 162 can be compressed and contracted to abut against each other in the circumferential direction of the second inner shaft 161 and press the second elastic component inwardly. The plurality of second outer shaft pieces 162 can also expand outward and separate from each other under the elastic force of the second elastic component.

[0102] This structure, which has a second inner shaft 161 inside and a plurality of second outer shaft pieces 162 that can shrink and expand outside, can ensure that the connecting pin 160 has a certain structural strength, and can also achieve expansion and shrinkage, so as to stably support the rotor. In addition, since the outer peripheral part is designed as a split body, the production cost is low, and it can be made of waste scraps to reduce costs. The number of the plurality of second outer shaft pieces 162 is at least two, including but not limited to three, four, etc.

[0103] Fig.13 A schematic diagram of the side view of the connecting pin 160 is shown. Fig.14 , Fig.15 and Fig.16 They are Fig.13 The figure is a cross-sectional view taken along the QQ direction, and is a cross-sectional view of the connecting pin 160 in different states.

[0104] Fig.14 A cross-sectional view of the connecting pin 160 in a natural state without being squeezed is shown. It can be seen that when the connecting pin 160 is not squeezed, the cross-section is substantially a perfect circle. Fig.15 The schematic diagram shows the connecting pin 160 in the process of being compressed. At this time, the second elastic component is compressed, and two adjacent second outer shaft sheets 162 have not yet completely abutted against each other. Fig.16 The cross-sectional schematic diagram of the connecting pin 160 in a compressed state is shown. At this time, any two circumferentially adjacent second outer shaft sheets 162 abut against each other, and the connecting pin 160 is compressed to a minimum state.

[0105] Here, the plurality of second outer shaft pieces 162 can be designed according to the maximum diameter, that is, when the connecting pin 160 is observed along the axial direction of the connecting pin 160, the connecting line of the outer contours of the plurality of second outer shaft pieces 162 in the natural state without compression is a circle. Therefore, after the second outer shaft pieces 162 are squeezed and contracted, the connecting line of the outer contours of the plurality of second outer shaft pieces 162 is non-circular and has a certain bulge, as shown in FIG. Fig.16 The connecting pin 160 has four bulges on the top, bottom, left and right sides, with the center position in the figure as the reference, which is similar to a square-circular structure. This structure can ensure buffering after the shaft-hole clearance deviation is large. Even if the connecting pin 160 rotates, it will get stuck due to the non-circular structure after rotating to a certain angle, thereby ensuring that the connecting pin 160 can stably withstand torque. Fig.14 and Fig.16 As shown, L5 is the lateral movement space of the second outer shaft piece 162, L6 is the minimum diameter of the second outer shaft piece 162 in the compressed state, L7 is the buffer area of ​​the second outer shaft piece 162, and L8 is the difference between the maximum adaptation diameter and the minimum adaptation diameter of the connecting pin 160. Therefore, in order to adapt to the plug holes on different generator rotors, the size of the buffer area can be set according to the above four parameters to ensure that the overall force of the connecting pin 160 is uniform and safe and reliable.

[0106] Regarding the specific structure of the second elastic component, in a specific embodiment, as Fig.12 , Fig.14 , Fig.15 and Fig.16 As shown, the second elastic component includes a plurality of second springs 163, and at least one second spring 163 is connected between any two circumferentially adjacent second outer shaft pieces 162. When the connecting pin 160 is compressed, two adjacent second outer shaft pieces 162 approach each other and squeeze the second spring 163. On the one hand, the second spring 163 can provide a supporting force to enable the connecting pin 160 to stably support the rotor, and on the other hand, it can also buffer the force impact of the connecting pin 160 and increase the service life of the connecting pin 160.

[0107] The second spring 163 may be a leaf spring, extending along the axial direction of the second inner shaft 161. The leaf spring takes up little space and is easy to install. Of course, the second spring 163 may not be a leaf spring, and multiple structures of this type may be used.

[0108] Two or more second springs 163 may be provided between two circumferentially adjacent second outer shaft pieces 162, and the two or more second springs 163 may be spaced apart in the radial direction of the second inner shaft 161, or spaced apart in the axial direction of the second inner shaft 161. This may increase the compression resistance of the connecting pin 160, and help keep the plurality of second outer shaft pieces 162 in an expanded state, rather than being prone to partial collapse due to failure of the second springs 163.

[0109] In addition, if Fig.14 , Fig.15 and 16 As shown, at least one of the two circumferentially adjacent end faces of the two circumferentially adjacent second outer shaft pieces 162 is provided with a spring receiving groove 1621, and the second spring 163 can be compressed and embedded in the spring receiving groove 1621, so that the two circumferentially adjacent second outer shaft pieces 162 are in contact with each other in the circumferential direction. The design of the spring receiving groove 1621 is convenient for accommodating the second spring 163, facilitating the full contact of the two adjacent second outer shaft pieces 162, and also conducive to limiting the deformation range of the second spring 163.

[0110] Of course, in other embodiments, the second spring 163 may also be replaced by other structures, such as an elastic rubber member or other damping devices that can achieve this function, which are also within the protection scope of the present application.

[0111] Furthermore, the second elastic component also includes a non-Newtonian fluid layer 164, which is wrapped around the outside of the second inner shaft 161 and can support multiple second outer shaft sheets 162 on the inside. Due to the material properties of non-Newtonian fluids, the greater the torque, the greater the reaction force, so there will be no problem of deformation and disengagement of the connecting pin 160. Moreover, there is no external load torque during installation and disassembly, and plugging and unplugging are extremely easy. During the load-carrying process, due to the characteristics of non-Newtonian fluids, it is strong when encountering rigidity and can transmit force very well. The non-Newtonian fluid layer 164 can buffer the buffering force during the installation of the pin and the rotation process under load.

[0112] Specifically, the non-Newtonian fluid layer 164 can be a polyvinyl chloride layer or a polyethylene layer. Of course, other non-Newtonian fluids can also be used instead (such as concentrated solutions and suspensions of high molecular polymers are generally non-Newtonian fluids. Polyethylene, polyacrylamide, polyvinyl chloride, nylon 6, PVS, celluloid, polyester, rubber solution, various engineering plastics, chemical fiber melts, solutions, etc. are all non-Newtonian fluids. Petroleum, mud, coal-water slurry, ceramic slurry, pulp, paint, ink, toothpaste, silk regeneration solution, drilling washing fluid and completion fluid, magnetic slurry, coatings of certain photosensitive materials, foams, liquid crystals, high sand content water flow, debris flow, mantle, etc. are also non-Newtonian fluids, etc.).

[0113] In a specific application, the non-Newtonian fluid layer 164 can be nested outside the second inner shaft 161, and the non-Newtonian fluid layer 164 is buffered and finally transmits the force to the second inner shaft 161. The second spring 163 is used to connect the plurality of second outer shaft pieces 162 into a whole, and the spring receiving groove 1621 is used to compress and store the second spring 163 after the plurality of second outer shaft pieces 162 are compressed to the minimum.

[0114] Regarding the specific structure of the second spring 163 component, in another specific embodiment, the second elastic component includes a plurality of second springs. Different from the above structure, each second spring is connected to the outer side of the second inner shaft 161 and the inner side of the second outer shaft sheet 162, and the second spring is used to support the second outer shaft sheet 162. The structure is similar to Fig. 9 When the connecting pin 160 is compressed, the second outer shaft sheet 162 directly presses the second spring inwards to achieve the radial change of the connecting pin 160.

[0115] In order to smoothly insert the connecting pin 160 into the insertion hole of the rotor, further, as Fig.13As shown, the cross-sectional area of ​​the end of the plurality of connecting pins 160 close to the second transmission gear 152 is larger than the cross-sectional area of ​​the end of the plurality of connecting pins 160 away from the second transmission gear 152. For example, the plurality of connecting pins 160 are in the form of a cone with one end larger than the other end. On the one hand, it is convenient for the connecting pins 160 to be smoothly inserted into the corresponding plug holes on the rotor, and on the other hand, it is conducive to making the connecting pins 160 abut against the plug holes, avoiding the connecting pins 160 from moving in the plug holes, thereby facilitating the connecting pins 160 to fully bear the torque and improving the operational reliability of the turning tool.

[0116] Here, the shaft-like structure surrounded by the plurality of second outer shaft pieces 162 may be made large at one end and small at the other end, or the shaft-like structure surrounded by the plurality of second outer shaft pieces 162 and the second inner shaft 161 may be made large at one end and small at the other end.

[0117] During the installation of the connecting pin 160 and the rotor, the small head of the connecting pin 160 is first inserted into the rotor plug hole. At this time, the shaft hole gap is large and there is a problem of eccentricity. When the connecting pin 160 is gradually pushed in (pushed toward the generator end), the second spring 163 is gradually compressed into the spring receiving groove 1621, and the polyvinyl chloride layer is gradually stressed. Because the reaction force is not large during the installation process, the installation can be gradually recommended. The large head of the connecting pin 160 gradually enters the inside of the rotor differential control to achieve seamless fitting installation. Finally, after the brake device is installed, all the plug holes and the connecting pin 160 are tightly connected, solving the problem of difficult installation of traditional pins with the same diameter at both ends.

[0118] Furthermore, the plurality of connecting pins 160 and the second transmission gear 152 are detachably connected, so that the connecting pins 160 can be easily replaced, and the connecting pins 160 can be prevented from being worn out over a long period of time and affecting the turning gear.

[0119] The connecting pin 160 can contract and expand radially, and is roughly push-shaped, so that the connecting pin 160 can be suitable for connecting with different generators. In addition, when the connecting pin 160 can also be detachably connected to the second transmission gear 152, it is also beneficial to replace different connecting pins 160 according to different types of generators, and connect to the ports of different types of generators. The braking device can be applied to various types of generators, realize the turning function of different manufacturers, different models, and different impeller loads, and greatly increase the versatility of the turning tool. According to the calculation of 1.5 million for a set of turning tool, the development of such a set of universal turning tool with a universal interface can be directly applied to future models above 20MW. It only needs to increase the diameter of the connecting pin 160, the diameter of the locking pin 130, and the torque of the drive motor 181. The cost is about 100,000, which is equivalent to purchasing a new set of turning tool, reducing costs.

[0120] In addition, the design of the connecting pin 160 of the present invention allows for free combination. In addition to being used to connect the rotor, it is also convenient for universal connection of the interface between the stator and rotor of generators from different manufacturers, and can also be used for the connection of the plug interface of old lifting equipment to achieve cost reduction of the lifting equipment. The connecting pin 160 is universal and multi-purpose, and the pin can adjust the gap radially. Of course, the pin can also be adjusted axially, which is convenient for mass production.

[0121] The second embodiment of the present invention provides a turning tool, including the brake device as described in the first embodiment. Here, the brake device is a part of the turning tool, and the brake device is used to drive the turning component to be turned to rotate during the turning process, and the brake device is used to control the turning component to be turned to stop rotating. Since the brake device has a good braking effect, it can effectively prevent the turning component from continuing to rotate after the turning stops, thereby improving the turning safety.

[0122] Furthermore, the turning tool further includes a detection module, which is used to detect the rotation parameters of the rotatable part and / or the rotation parameters of the brake disc 110. The detection module can be used to timely understand the turning condition of the turning tool and timely discover whether the turning tool has a fault.

[0123] In a specific application, the rotation parameter may be the rotation speed, or may be other parameters that can reflect the size of the rotation speed.

[0124] The detection module may have only one detection device, and only detect the rotation parameters of the rotatable part, or only detect the rotation parameters of the brake disc 110, so as to reduce parts and save costs.

[0125] like Figure 3 and Figure 5 As shown, the detection module may also have two detection devices, namely a first detection device and a second detection device, the first detection device is used to detect the rotation parameters of the brake disc 110, and the second detection device is used to detect the rotation parameters of the rotatable part. Monitoring the rotation of the turning tool at two positions can realize redundant monitoring of the turning condition and high-precision monitoring, which is conducive to timely detection of the turning problem after a turning failure occurs.

[0126] As an example, the first detection device is a laser sensor 212, which is used to detect the time taken by the brake disc 110 to rotate to a set central angle. The bracket 120 is provided with a plurality of through holes, which are distributed around the center of the brake disc 110 at intervals of a set central angle, and the laser sensor 212 is arranged relative to the positions of the plurality of through holes. By sensing the plurality of through holes, the time taken by the brake disc 110 to rotate to a set central angle is detected. The second detection device is a rotary encoder 211, which is used to detect the rotation angle of the second transmission gear 152 within a set time.

[0127] Of course, the first detection device and the second detection device may also be other sensors to detect the rotation speed of the brake disc 110 and the like.

[0128] Furthermore, the turning gear tooling also includes a control module (not shown in the figure). The control module here can be independent of the wind turbine generator set, or can be the same structure as the control device of the wind turbine generator set.

[0129] The control module is used to control the locking bolt driver according to the detection result of the detection module.

[0130] The control module is also used to control the brake disc drive according to the detection result of the detection module.

[0131] The control module is also used to control the clamp driving member according to the detection result of the detection module.

[0132] The control module here is a general term for the control structure, which does not mean that one control structure must control three driving components. Multiple control structures can also control the locking pin driving component, the brake disc driving component and the clamp driving component respectively. Multiple control structures can be set at different positions or assembled together.

[0133] Regarding the specific control method of the control module, in some embodiments, when the detection module can detect the rotation parameters of the rotatable part and the rotation parameters of the brake disc 110, the control module can control one or more of the locking latch driver, the brake disc driver, and the clamp driver according to any of the rotation parameters of the rotatable part and the brake disc 110. When the detection module finds that there is a problem with the turning gear, braking or other adjustments can be performed in time.

[0134] As an example, when any of the rotation parameters of the rotatable part and the rotation parameters of the brake disc 110 is lower than the corresponding set range, the control module sends a brake signal to the clamp driver to drive the brake clamp 140 to brake. At this time, the turning tool may rotate too slowly, and the brake disc 110 can be stopped by using the brake clamp 140 to brake, which is simple to operate. Before the brake clamp 140 is braked, the control module can also send a deceleration signal to the brake disc driver to drive the brake disc 110 to rotate at a speed lower than the preset speed. Therefore, after the brake disc 110 decelerates and rotates, the brake clamp 140 is driven to brake, which is conducive to the rapid stop of the brake disc 110.

[0135] When the rotation parameters of the rotatable part and the rotation parameters of the brake disc 110 are both within the corresponding set ranges, the control module controls the brake disc 110 to continue rotating. At this point, it means that there is no fault in the turning tooling, and the control module can send a full-speed signal to the brake disc driver to drive the brake disc 110 to rotate at a preset speed to continue turning. Until the brake disc 110 rotates to the set angle, the brake disc 110 is controlled to stop rotating. Here, the brake disc driver can be used to stop driving the brake disc 110 to rotate, or the brake caliper 140 can be controlled in conjunction with the clamp driver to brake the brake disc 110. After the brake disc 110 stops rotating, the locking pin driver can be controlled to drive the locking pin 130 to insert into the socket 111 of the brake disc 110 to lock the brake disc 110, thereby preventing the turning tooling from continuing to turn and rotate, affecting safety.

[0136] It should be noted that after the brake disc 110 stops rotating, when the turning tool is loaded, even if the brake caliper 140 clamps the brake disc 110, due to the heavy blades, when the blades are not in a vertical state, the brake disc 110 will rotate a certain angle under the action of the torque brought by the load, thereby facilitating the locking pin 130 to be inserted into the socket 111.

[0137] When any one of the rotation parameters of the rotatable part and the rotation parameters of the brake disc 110 is higher than the corresponding set range, the control module sends a brake signal to the clamp driver to drive the brake clamp 140 to brake, and sends a lock signal to the lock pin driver to drive the lock pin 130 to insert into the socket 111 during the deceleration process of the brake disc 110. At this time, the turning tool may have the problem of too fast speed, which poses a great safety hazard. Therefore, the brake clamp 140 is emergency braked, and the lock pin 130 is inserted into the brake disc 110 during the deceleration process of the brake disc 110, so that the brake disc 110 can be stopped quickly and stably, reducing the safety hazard. Here, the lock pin 130 is extended during the deceleration process of the brake disc 110, which increases the probability of the lock pin 130 inserting into the socket 111 on the one hand, and reduces the wear of the lock pin 130 and the brake disc 110 on the other hand, and avoids the lock pin 130 from being inserted into the high-speed rotation process of the brake disc 110, which has a great impact on the brake disc 110.

[0138] In addition, in this case, the control module can also send a stop signal to the brake disc driver to stop driving the brake disc 110 to rotate, and cooperate with the brake caliper 140 and the locking pin 130 to ensure that the brake disc 110 stops rotating in time.

[0139] Regarding the specific control method of the control module, in other embodiments, when the detection module is capable of detecting the rotation parameters of the rotatable part and the rotation parameters of the brake disc 110, the control module can control one or more of the locking pin driver, the brake disc driver and the clamp driver according to the rotation parameters of the rotatable part and the rotation parameters of the brake disc 110.

[0140] As an example, when the rotation parameters of the rotatable part and the rotation parameters of the brake disc 110 are both within the corresponding set range, the control module controls the brake disc 110 to continue rotating. At this time, it means that there is no fault in the turning tool, and the control module can send a full-speed signal to the brake disc driver to drive the brake disc 110 to rotate at a preset speed to continue turning. Until the brake disc 110 rotates to the set angle, the brake disc 110 is controlled to stop rotating. Here, the brake disc driver can be used to stop driving the brake disc 110 to rotate, and the brake caliper 140 can be controlled to brake the brake disc 110 in cooperation with the clamp driver. After the brake disc 110 stops rotating, the locking pin driver can be controlled to drive the locking pin 130 to insert into the socket 111 of the brake disc 110 to lock the brake disc 110, so as to prevent the turning tool from continuing to turn and rotate, affecting safety.

[0141] When one of the rotation parameters of the rotatable part and the rotation parameters of the brake disc 110 is not within the corresponding setting range, the control module sends a brake signal to the clamp driver to drive the brake clamp 140 to brake. Since one of the rotation parameters of the rotatable part and the rotation parameters of the brake disc 110 is not within the corresponding setting range, and the other is within the corresponding setting range, it means that the turning tooling has a fault, but the impact caused by the fault is not large at present. Therefore, in this case, the brake clamp 140 can be used to stop the brake disc 110, which is simple to operate. Of course, before the brake clamp 140 is braked, the control module can also send a deceleration signal to the brake disc driver to drive the brake disc 110 to rotate at a speed lower than the preset speed, so that when the brake disc 110 is decelerated, the brake clamp 140 is driven to brake, which is conducive to the rapid stop of the brake disc 110 and reduces wear.

[0142] When the rotation parameters of the rotatable part and the rotation parameters of the brake disc 110 are not within the corresponding set range, the control module sends a brake signal to the clamp driver to drive the brake clamp 140 to brake, and sends a locking signal to the locking pin driver to drive the locking pin 130 to insert into the socket 111 during the deceleration of the brake disc 110. In this case, it means that the turning tooling has a fault and continuously affects the rotation parameters of the two positions. Therefore, emergency braking is required to avoid major problems. Therefore, the brake clamp 140 is emergency braked, and the locking pin 130 is inserted into the brake disc 110 during the deceleration of the brake disc 110, so that the brake disc 110 can be stopped quickly and stably, reducing safety hazards. Here, the locking pin 130 is extended during the deceleration of the brake disc 110, which increases the probability of the locking pin 130 inserting into the socket 111 on the one hand, and can reduce the wear of the locking pin 130 and the brake disc 110 on the other hand, and avoids the locking pin 130 from being inserted during the high-speed rotation of the brake disc 110, which has a greater impact on the brake disc 110.

[0143] In addition, in this case, the control module can also send a stop signal to the brake disc driver to stop driving the brake disc 110 to rotate, and cooperate with the brake caliper 140 and the locking pin 130 to ensure that the brake disc 110 stops rotating in time.

[0144] Of course, in other embodiments, when the detection module can only detect the rotation parameters of the rotatable part or the rotation parameters of the brake disc 110, the control module can also control one or more of the locking pin driver, the brake disc driver and the clamp driver according to the detected parameters.

[0145] In addition, referring to the above embodiment, the control module can control the brake disc 110 to continue rotating when the rotation parameter detected by the detection module is within the set range. The control module can also control the brake caliper 140 to engage the brake when the rotation parameter detected by the detection module is not within the set range, and control the locking pin 130 to insert into the socket 111 of the brake disc 110 during the deceleration process of the brake disc 110. Or the control module can also control the brake caliper 140 to engage the brake when the rotation parameter detected by the detection module is lower than the set range, and control the brake caliper 140 to engage the brake when the rotation parameter detected by the detection module is higher than the set range, and control the locking pin 130 to insert into the socket 111 of the brake disc 110 during the deceleration process of the brake disc 110.

[0146] The following is a detailed description of a turning tool of an embodiment of the present invention. The turning tool provides a connecting pin 160 that can be radially contracted and expanded, a turning tool load locking mechanical structure, and a turning tool load control logic, which can be applied to medium-speed permanent magnet units, semi-direct drive units, and direct drive units. Impeller load mechanical locking and electrical control logic.

[0147] The following describes the components and their functions in the turning tooling. Figure 3 As shown, the first transmission gear 151 is provided with a mounting hole on its upper part. The connecting pin 160 is characterized by a conical structure and can shrink and expand in the radial direction, so as to realize seamless connection with the plug hole on the generator rotor. The support seat 170 is provided with a support shaft 171, and the support shaft 171 is sleeved with a shaft sleeve 172 and an end face flange 173. The end of the support shaft 171 is inserted into the center hole of the second transmission gear 152 and fixed, so that the second transmission gear 152 rotates and drives the whole to rotate. The connecting shaft 112 is installed on the brake disc 110, and the front end of the brake disc 110 is provided with a first transmission gear 151, and the first transmission gear 151 is meshed with the second transmission gear 152 to transmit power. The bracket 120, a part of the brake disc 110 is located inside the bracket 120. The brake caliper 140 is arranged on the bracket 120 and is used for friction braking of the brake disc 110. The brake disc 110 and the brake caliper 140 are used for load adjustment and stepless mechanical control of the turning wheel rotation structure. The brake disc drive component includes two drive motors 181 and two gear boxes 182. There are two brake discs 110. The connecting shafts 112 on the two brake discs 110 are connected to a drive motor 181 through a gear box 182, so that the drive motor 181 drives the brake disc 110 to rotate through the gear box 182. The two drive motors 181 can be driven at the same time, or one of them can be driven independently. They can be operated at full power to rotate the brake disc 110 at a preset speed, or they can be operated at half power to rotate the brake disc 110 at half the speed to ensure that the driving force meets the redundancy requirements. The gear box 182 is used to adjust the reduction ratio to achieve torque load adjustment. At the same time, the rotation parameters of the second transmission gear 152 are monitored by the rotary encoder 211 and the rotation parameters of the brake disc 110 are monitored by the laser sensor 212. Double detection and redundant feedback control ensure that the load adjustment logic control of the winch is meticulous and that no safety problems occur. The protective cover 190 is used to protect the mechanical structure of the winch tooling against rain and corrosion, and the structure can be adapted to the size and shape of the box. Reference Figure 3 The second transmission gear 152 , the brake disc 110 , the brake caliper 140 , the brake disc driving member and other structures are all arranged on the inner side of the protective cover 190 .

[0148] The turning tooling proposed in this embodiment, the connecting pin 160 can be used to meet the connection requirements of generator ports of different models, ensuring smooth installation of interfaces of different models. At the same time, the connecting pin 160 is evenly stressed, and the problem of single pin breakage will not occur. This structure is relatively important. Due to the trend of reducing costs, all main engine manufacturers currently cancel the brake disc 110 structure of the original unit. Once the pin connected to the generator breaks, the impeller rotation will become uncontrollable. This embodiment can perfectly solve this problem through the design of a conical connecting pin 160. In addition, since the current unit does not have a brake disc 110, all braking needs to be borne by the turning machine tooling body. Therefore, the present structure is designed with a micro brake disc 110 structure, specifically a self-locking brake disc 110 structure. Through the design of the brake disc 110 socket 111 and the locking pin 130, the brake disc 110 is used to slow down the rotation speed of the loaded turning machine. At the same time, through the evenly distributed specific socket 111 hole position, the locking pin 130 is inserted from the big head end 1111, and with the help of the rotation of the brake disc 110, the locking pin 130 is squeezed to achieve buffered locking of the pin. At the same time, the hole position of the socket 111 becomes smaller. After the buffer zone ends, it can be accurately positioned and locked to ensure the safe locking of the turning machine with load. At the same time, a sensor monitors the angular interval of the second transmission gear 152 rotating for a specific time, and another sensor monitors the time interval used for the brake disc 110 to rotate at a specific angle, thereby controlling the insertion and withdrawal of the locking pin 130 and the full-power and reduced-power operation of the brake disc drive. This logically provides safe and controllable protection, ensures automatic control of the brake wheel with load, and reduces the risk of human error.

[0149] Specifically, when the turning tool fails to load, the hydraulic drive structure (a type of clamp drive) first drives the brake caliper 140 to engage the brake, so that the rotation speed of the brake disc 110 decreases, and at the same time, the feedback control module drives the locking pin 130 to start pushing forward. The brake disc 110 can be provided with 6-8 pairs of sockets 111, which are used to achieve mechanical locking of the locking pin 130 at different angles. After the locking pin 130 penetrates the first avoidance hole 1211 on one side of the bracket 120, it passes through the through hole 141 on the brake caliper 140, and then passes through the socket 111 on the brake disc 110 and is inserted into the second avoidance hole 1221 on the other side of the bracket 120 to achieve mechanical locking of the brake disc 110. Preferably, the number of the locking pins 130 is more than two, which are redundant with each other, and a single locking pin 130 itself can withstand the mechanical locking of the turning tool load.

[0150] The specific implementation process is as follows: when the detection module detects that the turning wheel has a fault, the brake caliper 140 starts to brake, and the friction resistance of the brake disc 110 increases. At the same time, the locking pin 130 penetrates into the brake disc 110 and the bracket 120. At this time, the brake disc 110 continues to rotate. After the locking pin 130 penetrates into the inside of the insertion hole 111 of the brake disc 110 (the large hole is designed to facilitate the smooth insertion of the locking pin 130), as the turning wheel tooling continues to rotate, the locking pin 130 is gradually compressed, and the first outer shaft piece 132 is gradually compressed and stressed, shrinking inward, and even forming a solid pin structure. When the position size corresponding to the insertion hole 111 and the locking pin 130 gradually becomes smaller, the force on the locking pin 130 gradually increases. At the same time, under the action of the continued rotation of the brake disc 110 under force, the belt-carrying turning wheel can be quickly braked, and the self-locking function can be realized. At the same time, the rotation angle is very small, which is dispersed to the gear box 182 with a transmission ratio of more than 100. The rotation angle of the impeller end is very small and can be considered to be in a static state, which can ensure the safety of the personnel working in the hub.

[0151] The following is an example of the winching of the winch tool during the process of hoisting the blade. First, power is supplied from the deck and the brake disc drive is turned on. After the self-inspection of the winch tool is completed, the winch tool can be lifted to be installed with the plug holes on the rotor of the unit generator. The plug holes are usually 4, 6 or 8 evenly distributed. The connecting pin 160 is plugged and connected with the plug holes. Usually, after the connecting pin 160 is installed, there will be a bolt connection. Since the rotational torque is mainly borne by the shear of the connecting pin 160, the bolt only needs to bear the deadweight of the axial winch itself. The method is relatively common and will not be described in detail in this scheme. Just fix the winch tool itself. After the winch tool is installed, the blade can be lifted and the hub interface of the winch installed blade is rotated to horizontal (this process is no-load). When the blade is lifted to the position, the blade is docked. When the blade bolt torque is tightened, the blade clamp can be loosened. At this time, the winch tool starts to rotate with load and rotates normally. This is a normal working condition and will not be described in detail. When the winch is abnormally loaded, the rotary encoder 211 and the laser sensor 212 control the brake clamp 140 through signal feedback, and control the locking pin 130 to penetrate into the brake disc 110, and adjust the operating power of the brake disc drive to prevent overload of the connecting shaft 112, so as to ensure that the loaded winch is braked quickly and smoothly, and ensure the safety of the operator and the unit construction personnel. When the winch fault is eliminated, the locking pin 130 is pulled out again, the brake clamp 140 is opened, and the wheel hub is driven to rotate again through the brake disc 110, the first transmission gear 151, the second transmission gear 152, and the rotor. Among them, the brake clamp 140 is driven by a hydraulic drive, and the electrical control of the brake disc drive and the locking pin 130 is a separate circuit, with redundant protection. If one line has a problem, the other method continues to keep the lock.

[0152] The control part of this embodiment has high stability through mature sensor technology and feedback mechanism, and is combined with redundant protection of brake disc drive parts to achieve stepless locking during the braking process of the loaded disc car. It can hover at a set angle to achieve precise control and ensure the safety of on-site operators and hoisting personnel. The mechanical structure of this embodiment has low manufacturing cost, simple electrical control components, high efficiency, mature principles, and greatly reduces the requirements for safety, reliability, and low cost in the development process of the disc car tooling. This solution can be applied to medium-speed permanent magnet units, as well as direct-drive units and double-fed units. As long as the generator end and the pin structure are connected, the loaded disc car, drive and locking functions can be realized, and the application prospects are broad.

[0153] The turning tool provided in this embodiment can solve the problem that the turning tool on the market cannot monitor and lock the turning tool in real time after the turning tool fails. It can also solve the safety problem of the large circumferential space of the drive shaft and the lack of redundant locking in the current electric-driven turning tool, and solve the problem of oil leakage risk and load stall in the current hydraulic-driven turning tool.

[0154] The third aspect of the present invention provides a wind turbine generator set, including the brake device provided in the first aspect of the present invention, or the turning tool provided in the second aspect of the present invention. The brake device is applied to the wind turbine generator set to brake a part of the structure of the wind turbine generator set.

[0155] Furthermore, the wind turbine generator set includes a generator and a hub connected to the generator, and the rotatable part of the brake device is detachably connected to the rotor of the generator. When turning is required, the brake device is used to drive the hub to rotate via the rotor, and when turning is not required, the brake device is separated from the rotor.

[0156] Although the embodiments of the present invention have been described in detail above, those skilled in the art may make various modifications and variations to the embodiments of the present invention without departing from the spirit and scope of the present invention. It should be understood that, in the opinion of those skilled in the art, these modifications and variations will still fall within the spirit and scope of the embodiments of the present invention defined by the claims.

Claims

1. A brake device, characterized in that: The brake device comprises: A brake disc (110), wherein a plurality of circumferentially distributed insertion holes (111) are provided on a disc surface of the brake disc (110); A locking module, the locking module comprising a bracket (120) and a locking pin (130), the locking pin (130) being movably arranged on the bracket (120) and being distributed relative to the positions of the plurality of insertion holes (111), the locking pin (130) being able to extend out and be inserted into one of the insertion holes (111).

2. The brake device according to claim 1, characterized in that: The locking pin (130) is capable of radial contraction and expansion.

3. The brake device according to claim 1, characterized in that: The locking latch (130) comprises: A first inner shaft (131); A plurality of first outer shaft sheets (132) are circumferentially distributed on the outer side of the first inner shaft (131) to surround the first inner shaft (131); and A first elastic component connects the first inner shaft (131) and the plurality of first outer shaft pieces (132); the plurality of first outer shaft pieces (132) can be compressed and contracted to abut against each other in the circumferential direction of the first inner shaft (131) and press the first elastic component inward; the plurality of first outer shaft pieces (132) can also expand outward and separate from each other under the elastic force of the first elastic component.

4. The brake device according to claim 3, characterized in that: The first elastic component comprises: A plurality of first springs (133) are respectively connected to the outer side of the first inner shaft (131) and the inner side of the first outer shaft sheet (132); or A plurality of first rubber pads are connected to the outer side of the first inner shaft (131) and the inner side of the first outer shaft sheet (132).

5. The brake device according to claim 4, characterized in that: Based on the situation that the first elastic component includes a plurality of first springs (133), the first spring (133) is a leaf spring, extending along the axial direction of the first inner shaft (131), and in the circumferential direction of the first inner shaft (131), at least one first spring (133) is connected between each first outer shaft leaf (132) and the first inner shaft (131); Based on the situation that the first elastic component includes a plurality of first rubber pads, the first rubber pads are in the shape of long strips and extend along the axial direction of the first inner shaft (131), and in the circumferential direction of the first inner shaft (131), at least one first rubber pad is connected between each first outer shaft piece (132) and the first inner shaft (131).

6. The brake device according to any one of claims 1 to 5, characterized in that: The insertion hole (111) is configured as an elongated hole extending along the circumference of the brake disc (110).

7. The brake device according to claim 6, characterized in that: The space enclosed by one end of the insertion hole (111) in the circumferential direction of the brake disc (110) is large, forming a large head end (1111), and the space enclosed by the other end of the insertion hole (111) in the circumferential direction of the brake disc (110) is small, forming a small head end (1112); When the brake disc (110) rotates from the direction of the small end (1112) of one of the insertion holes (111) to the direction of the large end (1111), the locking pin (130) can be inserted into the insertion hole (111) through the large end (1111) and then squeezed and contracted to abut against the small end (1112); When the brake disc (110) rotates from the direction of the large end (1111) of one of the insertion holes (111) toward the direction of the small end (1112), the locking pin (130) can be inserted into the insertion hole (111) and abut against the large end (1111).

8. The brake device according to claim 7, characterized in that: The width of the insertion hole (111) in the radial direction of the brake disc (110) gradually decreases from the large end (1111) to the small end (1112); The outer diameter of the locking pin (130) in a natural state is smaller than the radial width of the large head end (1111) of the brake disc (110), and is larger than the radial width of the small head end (1112) of the brake disc (110).

9. The brake device according to claim 7, characterized in that: The inner end surface of the large head end (1111) is a first arcuate surface, and the first arcuate surface can contact the outer surface of the locking pin (130) in a natural state; and / or The inner end surface of the small head end (1112) is a second arc-shaped surface, and the second arc-shaped surface can contact the outer surface of the locking pin (130) in a retracted state.

10. The brake device according to any one of claims 7 to 9, characterized in that: The plurality of sockets (111) are distributed in a plurality of circles around the rotation center line of the brake disc (110); in each circle of the sockets (111), the large end (1111) of any one of the sockets (111) is close to the small end (1112) of the adjacent socket (111); and in two radially adjacent circles of the sockets (111), the large end (1111) of one circle of the sockets (111) faces in a clockwise direction, while the large end (1111) of the other circle of the sockets (111) faces in a counterclockwise direction; The number of the locking pins (130) is plural, and each circle of the insertion holes (111) is arranged opposite to at least one locking pin (130).

11. The brake device according to any one of claims 1 to 5, characterized in that: The bracket (120) comprises a first baffle (121) and a second baffle (122), wherein the first baffle (121) and the second baffle (122) are respectively located on two sides of the brake disc (110), the first baffle (121) is provided with a first avoidance hole (1211), and the second baffle (122) is provided with a second avoidance hole (1221), the insertion hole (111) is a through hole, and the locking pin (130) can pass through the insertion hole (111) through the first avoidance hole (1211) and then be inserted into the second avoidance hole (1221).

12. The brake device according to any one of claims 1 to 5, characterized in that: The locking module further comprises a locking pin driving member, wherein the locking pin driving member is used to push the locking pin (130) into the insertion hole (111) and drive the locking pin (130) to move out of the insertion hole (111); The brake device further comprises a brake module, which is arranged outside the brake disc (110), and the brake module can perform friction braking on the brake disc (110).

13. The brake device according to any one of claims 1 to 5, characterized in that: The brake device also includes: A first transmission gear (151), wherein the first transmission gear (151) is connected to the brake disc (110); The second transmission gear (152) is meshed with the first transmission gear (151), and a plurality of connection pins (160) are provided on one side of the second transmission gear (152), and the plurality of connection pins (160) are used for plug-in connection with the rotor of the generator.

14. The brake device according to claim 13, characterized in that: The cross-sectional area of ​​one end of the plurality of connecting pins (160) close to the second transmission gear (152) is larger than the cross-sectional area of ​​one end of the plurality of connecting pins (160) far from the second transmission gear (152); and / or The plurality of connecting pins (160) are capable of contracting and expanding in radial direction; and / or The plurality of connecting pins (160) and the second transmission gear (152) are detachably connected.

15. The brake device according to claim 13, characterized in that: Each of the connecting pins (160) comprises: A second inner shaft (161); A plurality of second outer shaft sheets (162) circumferentially distributed on the outer side of the second inner shaft (161) to surround the second inner shaft (161); and A second elastic component connects the second inner shaft (161) and the plurality of second outer shaft sheets (162). The plurality of second outer shaft sheets (162) can be compressed and contracted to abut against each other in the circumferential direction of the second inner shaft (161) and press the second elastic component inwardly. The plurality of second outer shaft sheets (162) can also expand outwardly and separate from each other under the elastic force of the second elastic component.

16. The brake device according to claim 15, characterized in that: The second elastic component comprises: A plurality of second springs (163) connected between two circumferentially adjacent second outer shaft pieces (162); A non-Newtonian fluid layer (164) is wrapped around the outer side of the second inner shaft (161) and is capable of supporting the plurality of second outer shaft sheets (162) on the inner side.

17. The brake device according to claim 16, characterized in that: The second spring (163) is a leaf spring and extends along the axial direction of the second inner shaft (161); The non-Newtonian fluid layer (164) is a polyvinyl chloride layer or a polyethylene layer.

18. The brake device according to claim 16, characterized in that: At least one of the two circumferentially adjacent end faces of the two circumferentially adjacent second outer shaft pieces (162) is provided with a spring receiving groove (1621), and the second spring (163) can be compressed and embedded in the spring receiving groove (1621) so that the two circumferentially adjacent second outer shaft pieces (162) are in contact with each other in the circumferential direction.

19. A turning tool, characterized in that: Comprising a brake device as claimed in any one of claims 1 to 18.

20. A wind turbine generator set, characterized in that: It comprises the braking device as described in any one of claims 1 to 18 or the turning tool as described in claim 19.

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