Rim sealing structure with flow guide function

Abstract

The invention discloses a rim sealing structure with a flow guide function, the rim sealing structure is arranged between a static disc and a movable disc, the rim sealing structure comprises at least one sealing piece annularly arranged on the movable disc, a channel communicated with a main flow channel and a disc cavity is arranged in the sealing piece, the channel comprises a first channel along the radial direction of the sealing piece, and a second channel along the radial direction of the sealing piece; the at least one second channel is arranged on the side face of the first channel, a first opening and a second opening of the second channel are both communicated with the first channel, the first opening is located in the side, facing the main flow channel, of the second opening, a first included angle is formed between the second channel and the first channel at the first opening, and a second included angle is formed between the second channel and the first channel at the second opening. The first included angle is smaller than 90 degrees, the second channel and the first channel form a second included angle at the second opening, and the second included angle is larger than 90 degrees. According to the rim sealing structure, the sealing effect is guaranteed, meanwhile, energy loss can be reduced, and the working efficiency of the gas turbine is improved.

Description

Technical Field

[0001] The invention relates to the field of gas turbines, and in particular to a wheel rim sealing structure with a flow guiding function. Background Art

[0002] Gas turbines play an important role in many key fields such as power generation, aviation propulsion and ship propulsion. With the advantages of rapid start and stop, quick load response, strong power output and outstanding efficiency, they have become the core power equipment to promote the development of various industries. According to the Brayton cycle theory, increasing the inlet temperature of the gas turbine is the key breakthrough to improve the efficiency of the gas turbine. However, the inlet temperature of the current international advanced level is approaching 2000℃, which is far beyond the heat resistance limit of the metal material itself. In such an extremely high temperature environment, the thermal stress and thermal load on the turbine components increase exponentially, which directly leads to a sharp reduction in their service life. Many studies have consistently shown that the intrusion of high-temperature gas is the main reason for the sharp increase in thermal stress of the turbine disc, and the rim sealing technology is the key to solving this dilemma.

[0003] The conventional practice of the existing rim sealing structure is to stagger several blocks on the sides of the static disk and the dynamic disk, and pass the cooling fluid at the bottom of the disk cavity to build a defense line to prevent high-temperature combustion gas from entering the disk cavity from the gap between the turbine moving blades and the turbine static blades. A similar structure is disclosed in Chinese invention patent CN107605543A. However, it cannot be ignored that the existing rim sealing exposes serious pressure loss problems in actual operation. First, in order to ensure that the cooling fluid can effectively resist the high-temperature combustion gas from the gap between the staggered blocks to enter the disk cavity, it is necessary to apply great pressure to the cooling fluid, which means a lot of energy investment. Second, when the cooling fluid hits the block at high speed, the kinetic energy of the airflow is rapidly converted into heat energy, turbulent energy and other invalid energy forms due to the collision and dissipated. Third, the cooling fluid has a large circumferential velocity relative to the dynamic disk, so when the cooling fluid enters the blade grid, there is a velocity component pointing to the suction side of the blade, which causes the cooling fluid to be strongly mixed with the mainstream fluid, causing aerodynamic losses of the mainstream fluid, and weakening the cooling effect of the cooling fluid on the hot end components such as the blades and end walls.

[0004] In summary, the energy loss problem caused by the existing wheel rim seal needs to be solved urgently. Summary of the invention

[0005] In order to overcome the defects in the prior art, an embodiment of the present invention provides a rim sealing structure with a flow guiding function, which can reduce pressure loss and improve the working efficiency of the gas turbine while ensuring the sealing effect.

[0006] In order to achieve the above object, the technical solution adopted by the present invention is:

[0007] In a first aspect, a rim sealing structure with a flow guiding function is provided between a static disk and a dynamic disk, and is characterized in that it comprises at least one sealing member arranged in an annular shape on the dynamic disk, wherein a channel connecting a main flow channel and a disk cavity is provided in the sealing member, wherein the channel comprises a first channel along a radial direction of the sealing member, and at least one second channel arranged on a side of the first channel, wherein a first port and a second port of the second channel are both connected to the first channel, wherein the first port is located on a side of the second port facing the main flow channel, wherein the second channel and the first channel form a first angle at the first port, wherein the first angle is less than 90°, and wherein the second channel and the first channel form a second angle at the second port, wherein the second angle is greater than 90°.

[0008] By setting a channel in the seal, the flow of the fluid can be guided so that the fluid in the seal rotates with the moving disk. Since the mainstream fluid enters the blade grid in the direction facing the leading edge of the moving blade (the angle of attack is 0°), the cooling fluid guided by the structure in the present application is consistent with the direction of the mainstream fluid when entering the blade grid channel, and the mixing between the mainstream fluid and the cooling fluid is weakened, which reduces the aerodynamic loss of the mainstream fluid and improves the cooling effect of the cooling fluid on the hot end components such as the moving blade grid blades and end walls.

[0009] And the channel includes a first channel extending radially along the seal and a second channel on the side of the first channel. In the gas turbine, the first channel can make the cooling fluid flow into the main channel more smoothly from one side of the disc cavity, reduce the pressure requirement for the cooling fluid to enter the main channel, thereby reducing external energy input, so that the gas turbine can use more energy for core work and improve thermal efficiency. At the same time, the cooling fluid can block the high-temperature mainstream fluid in the main channel from invading the disc cavity, protect the impeller from high temperature and high pressure impact, avoid thermal deformation and material degradation of the impeller, ensure the stability of the impeller structure, reduce maintenance costs, and extend the life of the gas turbine. Due to the setting of the angle between the second channel and the first channel, the second channel can guide the mainstream fluid to flow back, the sharp inlet angle allows the mainstream fluid to cut in smoothly, reduce turbulence and pressure loss, and the obtuse outlet angle ensures smooth reflux, maintains the stability of the fluid volume and flow rate of the main channel, ensures stable work of the gas turbine, and improves the reliability of the whole machine operation.

[0010] Preferably, the seal includes at least a first seal located at the edge of one end of the moving disk near the main flow channel. The edge of one end of the moving disk near the main flow channel is in the gap between the moving disk and the static disk. When the gas turbine is running, the main flow channel airflow has high energy and complex operating conditions. The first seal is arranged in the gap between the moving disk and the static disk that constitute the impeller, which can serve as the first barrier to face the impact of the mainstream fluid, prevent the mainstream fluid from entering the disc cavity, stabilize the fluid environment of the disc cavity, reduce the impact degree of internal components, reduce the risk of damage, extend the life of the impeller, maintain the conditions for efficient operation of the gas turbine, and reduce energy waste and performance degradation caused by sealing problems.

[0011] Further preferably, the seal also includes at least one second seal located in the disc cavity formed by the moving disc and the stationary disc. Specifically, the second seal can be arranged at one end of the disc cavity close to the main flow channel. On the basis of the first seal, the second seal is further provided to further block the mainstream fluid in the main flow channel from entering the disc cavity, thereby improving the sealing effect. Taking into account the actual situation, the number of the second seals can be set to be multiple. For example, at one end of the disc cavity close to the main flow channel, two second seals are spaced apart. The distance between adjacent second seals can be adjusted according to the disc cavity volume, the flow conditions of the mainstream fluid, the temperature, etc.

[0012] Preferably, the seal includes a plurality of the channels, and the plurality of channels are arranged in a circumferential manner along the seal. Further preferably, the plurality of channels are evenly arranged and distributed along the circumferential direction of the seal. The use of such a multi-channel surrounding layout structure has significant advantages. Under actual working conditions, when the high-temperature mainstream fluid and the low-temperature cooling fluid flow inside the seal at the same time, the two can be evenly distributed around the seal by virtue of the uniform surrounding arrangement of the channels. This ensures that the moving disk that cooperates with the seal can be heated evenly, effectively avoiding local overheating. This reduces the vibration of the moving disk caused by uneven heating, alleviates the problem of thermal stress concentration, prevents components from being damaged due to long-term excessive thermal fatigue and mechanical fatigue, greatly improves the reliability and operational stability of the entire system, and extends the service life of the equipment.

[0013] The shape of the first channel has many possibilities, it can be S-shaped, arc-shaped, or any other shape. The key point is that as long as the overall direction of the channel is from the disc cavity to the main channel, the basic requirement of the cooling fluid flowing smoothly into the main channel can be achieved. If the first channel is designed to be curved, it can guide the flow of the fluid to a certain extent, thereby reducing the pressure loss caused by the collision of the fluid with the seal during the flow process.

[0014] However, after comprehensive consideration and optimization, the preferred solution is to design the first channel to be linear. This is because the linear first channel can minimize the resistance encountered by the cooling fluid when it is transmitted inside the seal. In this case, the linear channel can more efficiently guide the cooling fluid to quickly enter the main channel, thereby effectively reducing the temperature of the wheel disc, and in the whole process, it can reduce unnecessary energy consumption as much as possible, thereby improving the operating efficiency and stability of the entire system.

[0015] The second channel has certain flexibility in shape design, and can be a ring or any other shape. However, no matter how its shape changes, it needs to meet specific angle conditions, that is, the first angle formed by the intersection with the first channel at the first opening must be an acute angle, and the second angle formed at the second opening should be an obtuse angle.

[0016] Among many optional shapes, after in-depth research and optimization screening, the preferred solution is to design the second channel into a curved shape with a water droplet profile. According to the principles of fluid mechanics, this curved shape of a water droplet profile can guide the mainstream fluid to turn and change speed in an extremely gentle way, effectively reducing the occurrence of turbulence. In terms of the interaction between the fluid and the channel wall, it can significantly optimize the relationship between the two, greatly reducing the frequency and intensity of friction and collision, thereby greatly improving the smoothness of fluid flow, so that the pressure loss can be effectively controlled at a low level. Through the careful design of the shape of the second channel, it can further ensure that the pressure loss of the mainstream fluid in the main channel is in a low state, thereby improving the thermal efficiency of the whole machine, reducing operating costs, and ultimately ensuring that the gas turbine can continue to operate stably and efficiently within its high efficiency range.

[0017] Preferably, the second channel is provided on both sides of the first channel. This double-sided setting can effectively increase the number of second channels. When the cooling fluid flows forward from one side of the disc cavity to the side of the main channel, although it also needs to bypass the second channel, thanks to the unique structure of the first channel, the cooling fluid can bypass the second channel along the first channel in a relatively smooth path, and the resistance encountered during the entire flow process is relatively small, so that the fluid can move forward more smoothly. In contrast, when the mainstream fluid flows in the opposite direction from one side of the main channel to one side of the disc cavity, the mainstream fluid will flow into each second channel. Due to the large number of second channels, the overall flow of the mainstream fluid to the disc cavity is greatly hindered, and the more the number of second channels, the greater the resistance encountered by the mainstream fluid when flowing to the disc cavity. This means that the smaller the additional pressure required for the cooling fluid to enter the main channel, the less energy is consumed accordingly.

[0018] In actual applications, the second channels on both sides have different arrangements. One feasible situation is that the second channels on both sides are arranged opposite to each other. Another possibility is that the second channels on both sides are arranged staggered with each other. The specific arrangement method can be flexibly adjusted according to the difficulty of the actual processing process, cost control and comprehensive consideration of fluid flow characteristics.

[0019] Preferably, the seal is composed of a plurality of blocks arranged in a ring shape, the first channel is formed between adjacent blocks, and the sides opposite to the adjacent blocks first extend into the blocks and then turn and extend back to the sides to form the second channel. The method of constructing the channel by block design is simple and convenient, and does not require complicated manufacturing processes and procedures, thereby making the processing process extremely convenient and quick. In actual application, if the number and size of the channels need to be adjusted, it is only necessary to change the number and size parameters of the blocks accordingly. This operation method is simple and easy, and can well meet the changes in different working conditions and design requirements. In addition, since each block is relatively independent, when facing a local airflow impact, each block can provide a certain degree of buffering capacity by virtue of its own structural characteristics, thereby effectively dispersing and absorbing the impact energy, reducing the risk of damage to the overall structure due to the local airflow impact, greatly improving the reliability and stability of the seal and even the entire system, and extending its service life and maintenance cycle.

[0020] Preferably, the surfaces of the block facing the main channel and the surfaces facing away from the main channel are both set as curved surfaces, and a guide port is formed between two adjacent curved surfaces. Specifically, the curved surface is semicircular, so that an eight-shaped guide port is formed between two adjacent curved surfaces. During the fluid transmission process of the seal, if the guide port is not set at the end of the block, a large-scale vortex phenomenon will be generated in the fluid at the outlet position of the first channel. The presence of this vortex will cause the resistance encountered by the cooling fluid when it flows from the first channel into the main channel to increase sharply. In order to overcome this resistance so that the cooling fluid can smoothly enter the main channel, a stronger pressure has to be applied to the cooling fluid, which will undoubtedly lead to a significant increase in pressure loss.

[0021] However, in the design proposed in the present application, by cleverly setting the end of the block as a curved surface, the flow path of the fluid can be effectively guided. When the fluid passes through the end of the block, the curved surface can guide the fluid so that its flow direction can be better maintained stable, thereby greatly reducing the formation of vortices. Due to the reduction in the number and intensity of vortices, the resistance of the fluid during the flow process is also significantly reduced, thereby achieving an effective reduction in pressure loss, which is of great significance for improving the operating efficiency and energy utilization of the entire system, and provides a strong guarantee for the efficient and stable operation of the system.

[0022] In a second aspect, a wheel disc sealing structure includes a stationary disc and a moving disc arranged opposite to each other, and the above-mentioned wheel rim sealing structure with a flow guiding function arranged on the moving disc.

[0023] In a third aspect, a gas turbine includes a stationary disk and a moving disk arranged relatively to each other, and the above-mentioned rim sealing structure with a flow guiding function arranged on the moving disk.

[0024] Due to the application of the above technical solution, the present invention has the following advantages compared with the prior art:

[0025] 1. In the present application, by setting a channel in the seal, the flow of the fluid can be guided so that the fluid in the seal rotates with the moving disk. Since the mainstream fluid enters the blade grid in the direction facing the leading edge of the moving blade (the angle of attack is 0°), the cooling fluid guided by the structure in the present application is consistent with the direction of the mainstream fluid when entering the blade grid channel, and the mixing between the mainstream fluid and the cooling fluid is weakened, which reduces the aerodynamic loss of the mainstream fluid and improves the cooling effect of the cooling fluid on the hot end components such as the blades and end walls of the moving blade grid.

[0026] 2. The first channel and the second channel are set at a specific angle, which can allow the cooling fluid to flow into the main channel with minimal transmission resistance, and can guide the mainstream fluid to flow back to the main channel to maintain a stable flow in the main channel. This process can effectively reduce the wheel temperature, reduce unnecessary energy consumption, and improve system operation efficiency and stability.

[0027] 3. Setting multiple seals between the static disk and the dynamic disk can enhance the sealing effect, improve system reliability and operation stability, and extend the service life of the equipment.

[0028] 4. The surfaces of the block facing the main channel and the surface facing away from the main channel are set as curved surfaces (such as a semicircular figure-eight guide port), which can effectively guide the fluid flow path, reduce the formation of vortices at the outlet of the first channel, reduce the fluid flow resistance, and reduce pressure loss, which is of great significance to improving the system operation efficiency and energy utilization, and ensure the efficient and stable operation of the system.

[0029] 5. The seal is composed of multiple blocks arranged in a ring to construct a channel. This method is simple and convenient, does not require complex manufacturing processes, and is easy to process. If the number and size of channels need to be adjusted, the number and size parameters of the blocks can be changed to meet different working conditions and design requirements.

[0030] In order to make the above and other purposes, features and advantages of the present invention more obvious and easy to understand, preferred embodiments are specifically cited below and described in detail with reference to the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0031] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0032] Figure 1 is a partial schematic diagram of a wheel disc sealing structure in an embodiment of the present invention;

[0033] Figure 2 yes Figure 1 Middle side schematic diagram;

[0034] Figure 3 It is a partial schematic diagram of the sealing member on the moving disk in the present invention;

[0035] Figure 4 yes Figure 3 Middle side schematic diagram;

[0036] Figure 5 yes Figure 3 A partial enlarged view of the middle part;

[0037] Figure 6 yes Figure 4 A partial enlarged view of point B in the middle.

[0038] The figure numbers of the above drawings are: 1, static disk; 2, dynamic disk; 3, disk cavity; 4, first sealing member; 5, second sealing member; 601, stopper; 6011, semicircular curved surface; 602, first channel; 603, second channel. DETAILED DESCRIPTION

[0039] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0040] Example: See Figures 1 to 6 As shown, a wheel rim sealing structure is arranged between a static disk 1 and a dynamic disk 2. The static disk 1 and the dynamic disk 2 are oppositely arranged circular rings. A main flow channel is provided outside the wheel disk composed of the static disk 1 and the dynamic disk 2, and a disk cavity 3 is provided inside the wheel disk. Figure 1The diagram is a schematic diagram of a structure formed by cutting along the radial direction of the wheel disc. The wheel rim sealing structure includes a first sealing member 4, which is annular and fits on the side of the moving disc 2 opposite to the static disc 1, and is located at the edge of the moving disc 2 close to one end of the main flow channel, that is, between the main flow channel and the disc cavity 3, and in the gap between the static disc 1 and the moving disc 2. A channel connecting the main flow channel and the disc cavity 3 is provided in the sealing member, and the channel includes a first channel 602 along the radial direction of the sealing member, and a second channel 603 provided on both sides of the first channel 602. The first port and the second port of the second channel 603 are both connected to the first channel 602, and the first port is located on the side of the second port facing the main flow channel. The second channel 603 and the first channel 602 form a first angle α at the first port, and the first angle α is less than 90°. The second channel 603 and the first channel 602 form a second angle β at the second port, and the second angle β is greater than 90°. Specifically, the first angle α can be set to 35°, and the second angle can be set to 145°.

[0041] In the gas turbine, the first channel 602 can make the cooling fluid flow more smoothly from one side of the disc cavity 3 into the main channel, reduce the pressure requirement for the cooling fluid to enter the main channel, thereby reducing external energy input, so that the gas turbine can use more energy for core work and improve thermal efficiency. At the same time, the cooling fluid can block the high-temperature mainstream fluid in the main channel from invading the disc cavity 3, protect the impeller from high temperature and high pressure impact, avoid thermal deformation and material degradation of the impeller, ensure the stability of the impeller structure, reduce maintenance costs, and extend the life of the gas turbine. Due to the setting of the angle between the second channel 603 and the first channel 602, the second channel 603 can guide the mainstream fluid to flow back, the sharp inlet angle allows the mainstream fluid to cut in smoothly, reduce turbulence and pressure loss, and the obtuse outlet angle ensures smooth reflux, maintains the stability of the fluid volume and flow rate of the main channel, ensures stable work of the gas turbine, and improves the reliability of the whole machine operation.

[0042] See also Figure 3 , 4 As shown, the first seal 4 includes a plurality of the channels, and the plurality of channels are evenly arranged and distributed along the circumferential direction of the first seal 4. With this multi-channel surrounding layout structure, when the high-temperature mainstream fluid and the low-temperature cooling fluid flow inside the seal, the two can be evenly distributed around the first seal 4 by virtue of the uniform surrounding setting of the channels. This ensures that the moving disk 2 matched with the seal can be heated evenly and effectively avoids local overheating. In addition, the vibration of the moving disk 2 caused by uneven heating is reduced, while the problem of thermal stress concentration is alleviated, and components are prevented from being damaged due to long-term excessive thermal fatigue and mechanical fatigue, which greatly improves the reliability and operational stability of the entire system and extends the service life of the equipment.

[0043] In a preferred embodiment, see Figure 6 As shown, the first channel 602 is in a straight line. The straight first channel 602 can minimize the resistance encountered by the cooling fluid when it is transmitted inside the seal. In this case, the straight channel can more efficiently guide the cooling fluid to quickly enter the main channel, thereby effectively reducing the temperature of the wheel disc, and reducing unnecessary energy consumption as much as possible in the whole process, thereby improving the operating efficiency and stability of the entire system.

[0044] The second channel 603 is in the shape of a water droplet profile. According to the principles of fluid mechanics, the curve of the water droplet profile can guide the mainstream fluid to turn and change speed in an extremely gentle manner, effectively reducing the occurrence of turbulence. In terms of the interaction between the fluid and the channel wall, it can significantly optimize the relationship between the two, greatly reducing the frequency and intensity of friction and collision, thereby greatly improving the smoothness of fluid flow and effectively controlling the pressure loss at a low level.

[0045] In a preferred embodiment, the second channels 603 on both sides are arranged in an interlaced manner. By simultaneously arranging the second channels 603 on both sides of the first channel 602, the number of the second channels 603 can be effectively increased. When the cooling fluid flows forward from one side of the disc cavity 3 to the side of the main channel, although it also needs to bypass the second channel 603, thanks to the unique structure of the first channel 602, the cooling fluid can follow the first channel 602 and bypass the second channel 603 in a relatively smooth path, and the resistance encountered during the entire flow process is relatively small, so that the fluid can move forward relatively smoothly. In contrast, when the mainstream fluid flows in the opposite direction from one side of the main channel to one side of the disc cavity 3, the mainstream fluid will flow into each second channel 603. Due to the large number of second channels 603, the overall flow of the mainstream fluid to the disc cavity 3 is greatly hindered, and the more the number of second channels 603, the greater the resistance encountered by the mainstream fluid when it flows to the disc cavity 3. This means that the smaller the additional pressure required for the cooling fluid to enter the main channel, the less energy is consumed accordingly. The second channels 603 on both sides are arranged alternately with each other, so that the distance between two adjacent second channels 603 can be shortened, so that the mainstream fluid can continuously reflux in the second channels 603 .

[0046] See also Figures 3 to 5 As shown, in a preferred embodiment, a second sealing member 5 is provided in the disc cavity 3 formed by the moving disc 2 and the stationary disc 1. The second sealing member 5 is provided at one end of the disc cavity 3 close to the main flow channel. On the basis of the first sealing member 4, the second sealing member 5 is provided to further block the mainstream fluid in the main flow channel from entering the disc cavity 3, thereby improving the sealing effect.

[0047] In a preferred embodiment, two second sealing members 5 are provided in the disc cavity 3. The second sealing member 5 has the same shape as the first sealing member 4, but has different sizes according to different installation positions.

[0048] See also Figure 5 As shown, the seal is composed of a plurality of blocks 601 arranged in a ring shape, the first channel 602 is formed between adjacent blocks 601, and the sides opposite to the adjacent blocks 601 first extend into the block 601 and then turn and extend back to the side to form the second channel 603. The method of constructing the channel by designing the block 601 is simple and convenient, and does not require complicated manufacturing processes and procedures, thereby making the processing process extremely convenient and quick.

[0049] In a preferred embodiment, both end surfaces of the stopper 601 are set as semicircular curved surfaces 6011. A guide port of the first channel 602 is formed between two adjacent semicircular curved surfaces 6011. By cleverly setting the end of the stopper 601 as a semicircular curved surface 6011, the flow path of the fluid can be effectively guided. When the fluid passes through the end of the stopper 601, the semicircular curved surface 6011 can guide the fluid so that its flow direction can be better maintained stable, thereby greatly reducing the formation of vortices. Due to the reduction in the number and intensity of vortices, the resistance of the fluid during the flow process is also significantly reduced, thereby achieving an effective reduction in pressure loss.

[0050] The present application also discloses a wheel disc sealing structure, comprising a stationary disc 1 and a moving disc 2 that are arranged opposite to each other, and a wheel rim sealing structure arranged on the moving disc 2 .

[0051] The present application also discloses a gas turbine, comprising a stationary disc 1 and a moving disc 2 that are arranged opposite to each other, and a wheel rim sealing structure arranged on the moving disc 2 .

[0052] The present invention uses specific embodiments to illustrate the principles and implementation methods of the present invention. The description of the above embodiments is only used to help understand the method of the present invention and its core idea. At the same time, for those skilled in the art, according to the idea of ​​the present invention, there will be changes in the specific implementation methods and application scope. In summary, the content of this specification should not be understood as a limitation on the present invention.

Claims

1. A wheel rim sealing structure with a flow guiding function, the wheel rim sealing structure is arranged between a stationary plate and a moving plate, characterized in that: It includes at least one sealing member arranged in an annular shape on the moving disk, wherein the sealing member is provided with a channel connecting the main channel and the disk cavity, wherein the channel includes a first channel along the radial direction of the sealing member, and at least one second channel arranged on the side of the first channel, wherein the first port and the second port of the second channel are both connected to the first channel, the first port is located on the side of the second port facing the main channel, the second channel and the first channel form a first angle at the first port, the first angle is less than 90°, and the second channel and the first channel form a second angle at the second port, the second angle is greater than 90°.

2. The wheel rim sealing structure with flow guiding function according to claim 1, characterized in that: The sealing member at least comprises a first sealing member located at an edge of one end of the moving plate close to the main flow channel.

3. The wheel rim sealing structure with flow diversion function according to claim 1, characterized in that: The sealing member further includes at least one second sealing member located in a disc cavity formed by the moving disc and the stationary disc.

4. The wheel rim sealing structure with flow diversion function according to claim 1, characterized in that: The invention comprises a plurality of the channels, and the plurality of the channels are arranged circumferentially along the sealing member.

5. The wheel rim sealing structure with flow diversion function according to claim 1, characterized in that: The first channel is in a straight line shape, and the second channel is in a curved line shape with a water drop profile.

6. The wheel rim sealing structure with flow guiding function according to claim 1, characterized in that: The second channel is provided on both sides of the first channel.

7. The wheel rim sealing structure with flow diversion function according to claim 1, characterized in that: The sealing member is composed of a plurality of blocks arranged in a ring shape, the first channel is formed between adjacent blocks, and the second channel is formed on the opposite sides of the adjacent blocks by first extending into the block and then turning and extending back to the side.

8. The wheel rim sealing structure with flow guiding function according to claim 7, characterized in that: The surfaces of the block facing the main flow channel and the surfaces facing away from the main flow channel are both configured as curved surfaces, and a guide port is formed between two adjacent curved surfaces.

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