Spiral pressurizing liquid sealing structure and flow passage component comprising same

Abstract

The utility model relates to the technical field of water pump sealing, in particular to a spiral pressurizing liquid sealing structure and a flow passage component comprising the same. Comprising a shaft sleeve, glands and liquid injection holes, the movable ring sleeves the outer side of the shaft sleeve and rotates synchronously with the shaft sleeve; the static ring is in sliding connection with the inner wall of the gland and does not rotate along with the shaft sleeve; one end surface of the moving ring is a first friction surface; one end surface of the static ring is a second friction surface; the first friction surface and the second friction surface abut against each other to form a friction surface; the movable ring is provided with a turbulent flow structure which is arranged on the outer side of the friction face in the radial direction of the movable ring. The length direction of the turbulent flow structure is inclined relative to the adjacent diameter in the opposite direction of rotation of the movable ring; the turbulent flow structure is additionally arranged in the movable ring, so that the resistance between the movable ring and liquid is increased when the movable ring rotates, the surrounding liquid generates a transverse vortex, cooling liquid in a friction surface is attracted to flow towards the vortex position, and the cooling liquid can flush the friction surface and flush out solid particles possibly existing on the friction surface when flowing in the friction surface.

Description

Technical Field

[0001] The utility model relates to the technical field of water pump sealing, in particular to a spiral pressurized liquid sealing structure and a flow-through component comprising the structure. Background Art

[0002] Mechanical seals are shaft sealing devices commonly used in rotating mechanisms. They ensure axial sealing while leaving the shaft with rotational freedom. The friction surface in a mechanical seal is a leak-prone point, and the friction surface relies on elastic force and medium pressure to maintain contact (dynamic sealing point, there is relative rotation between the two friction pairs);

[0003] The friction surface leakage point is in the centrifugal pump. Due to the different liquid media, there are solid particles in the liquid, especially a large amount of sand in the impurity pump. When the sand enters the friction surface of the mechanical seal, it is easy to scratch the friction surface, resulting in gaps between the friction surfaces, causing the mechanical seal device to lose its sealing effect, thereby reducing the service life of the equipment. When the friction surface rotates, there is a probability that sand will enter the gap of the friction surface, and the fluidity of the liquid around the friction surface is poor, which causes a large amount of sand to accumulate around the friction surface. Too many sand particles will make it easier for sand particles to enter the gap of the friction surface and damage the friction surface. Utility Model Content

[0004] In order to solve the above-mentioned existing technical problems, the utility model provides a spiral pressurized liquid sealing structure, including a shaft sleeve, a gland, and a liquid injection hole;

[0005] A moving ring, fixedly sleeved on the outer side of the shaft sleeve, and rotating synchronously with the shaft sleeve;

[0006] A stationary ring connected to the inner wall of the gland and not rotating with the shaft sleeve;

[0007] The shaft sleeve drives the moving ring to rotate relative to the stationary ring.

[0008] The dynamic ring and the static ring rub against each other, wherein the friction surface of the dynamic ring is a first friction surface;

[0009] The friction surface of the stationary ring is the second friction surface;

[0010] Wherein, the dynamic ring has a flow-disturbing structure, and the flow-disturbing structure is arranged around the first friction surface in a radial direction;

[0011] Wherein, the length direction of the spoiler structure is inclined relative to the adjacent diameter in the opposite direction of the rotation of the moving ring;

[0012] The adjacent diameter is: a diameter of the first friction surface passing through the end point of the spoiler structure close to the center of the first friction surface;

[0013] Wherein, the outer circumferential wall surface of the moving ring has a flow-guiding thread;

[0014] The thread rotation direction of the guide thread is opposite to the rotation direction of the dynamic ring, so as to guide the liquid around the dynamic ring along the axis in a direction away from the first friction surface;

[0015] The sealing seat is fixedly connected to the gland and sleeved to the outer side of the static ring, and a sealing ring is provided between the sealing seat and the static ring;

[0016] Wherein, one end of the sealing seat has a cylindrical structure, and the cylindrical structure wraps around the guide thread;

[0017] Furthermore, the inner diameter of the cylindrical structure is 1.05-1.2 times the outer diameter of the guide thread.

[0018] Furthermore, the spoiler structure is configured as a spoiler groove recessed in the first friction surface;

[0019] The length of the spoiler groove is L1, and the width of the first friction surface is L2;

[0020] L1 <L2;

[0021] The width of the first friction surface is: the distance between the outer circle radius and the inner circle radius of the first friction surface;

[0022] Wherein, the starting end of the spoiler groove in the length direction passes through the outer circumferential wall surface of the dynamic ring;

[0023] The starting end of the spoiler groove in the length direction forms a spoiler area;

[0024] The remaining length area forms a guide area to guide the coolant in.

[0025] Furthermore, the second friction surface is concave to form a jet groove;

[0026] When the spoiler groove rotates with the moving ring and overlaps with the projection of the jet groove toward the first friction surface, the spoiler groove and the jet groove form a jet cavity;

[0027] Wherein, the liquid in the jet cavity enters the spoiler groove as the spoiler groove rotates, and is squeezed to form a jet in the diameter direction.

[0028] Furthermore, the outer diameter of the dynamic ring is greater than the outer diameter of the static ring, so that the starting end of the spoiler groove in the length direction protrudes from the outer wall surface of the static ring.

[0029] Furthermore, the depth of the spoiler groove is H1;

[0030] Among them, 0.3mm ​

[0031] Furthermore, the width of the spoiler groove is L3;

[0032] Among them, 0.5mm <L3<1mm;

[0033] The number of the spoiler grooves is N1;

[0034] Among them, 25 <N1<60。

[0035] Furthermore, the dynamic ring and the static ring are made of pressureless sintered silicon carbide.

[0036] Further, the shaft sleeve has a mounting hole;

[0037] The axis of the mounting hole is parallel to the axis of the sleeve;

[0038] A cylindrical transmission pin is fixedly arranged in the mounting hole;

[0039] The inner wall surface of the moving ring has an arc-shaped transmission groove;

[0040] The transmission groove is coaxially matched with the transmission pin so that the movable ring rotates synchronously with the shaft sleeve.

[0041] Further, comprising a spiral pressurized liquid sealing structure as described above, the flow-through component comprises:

[0042] Pump housing;

[0043] An impeller disposed in a pump casing;

[0044] A transmission shaft driving the impeller to rotate;

[0045] The shaft sleeve of the spiral pressurized liquid sealing structure is sleeved with the transmission shaft;

[0046] A pump cover, connected to the pump housing and located on the end surface opposite to the water inlet of the pump housing;

[0047] The gland of the spiral pressurized liquid sealing structure is connected to the pump cover.

[0048] The beneficial effect of the utility model is reflected in that a turbulent structure is added to the dynamic ring in the present application, so that the resistance between the dynamic ring and the liquid is increased when rotating, so that the liquid around the turbulent structure generates a lateral vortex, attracting the coolant in the friction surface to flow toward the vortex position, and the coolant can flush the friction surface when flowing in the friction surface, flushing out solid particles that may exist in the friction surface; when the coolant flows around the first friction surface, it can drive the medium liquid and solid particles to flow toward the surrounding area away from the friction surface, avoiding solid particles from entering the friction surface, scratching the first friction surface and the second friction surface, and causing failure of the sealing structure. BRIEF DESCRIPTION OF THE DRAWINGS

[0049] Figure 1 A schematic cross-sectional view of a spiral pressurized liquid sealing structure provided by the utility model;

[0050] Figure 2 for Figure 1 A local enlarged schematic diagram of point a;

[0051] Figure 3 A three-dimensional schematic diagram of the cylinder structure provided by the utility model;

[0052] Figure 4 This is a schematic diagram of the three-dimensional structure of the dynamic ring provided by the utility model;

[0053] Figure 5 A three-dimensional structural schematic diagram of another structure of a moving ring provided by the utility model;

[0054] Figure 6 It is a front view of the first friction surface of the dynamic ring;

[0055] Figure 7 A three-dimensional structural schematic diagram of the static ring provided by the utility model;

[0056] Figure 8 is a schematic diagram of the jet cavity;

[0057] Fig. 9 This is a schematic structural diagram of the flow-through component provided by the utility model.

[0058] Reference numerals:

[0059] 1. Moving ring; 11. First friction surface; 12. Disturbing structure; 13. Disturbing groove; 131. Disturbing area; 132. Guide area; 14. Guide thread; 2. Stationary ring; 21. Second friction surface; 22. Jet groove; 23. Jet cavity; 41. Mounting hole; 42. Transmission pin; 43. Transmission groove; 51. Bushing; 52. Pressure cover; 53. Injection hole; 54. Pump casing; 55. Impeller; 551. Balance hole; 56. Transmission shaft; 57. Pump cover; 6. Adjacent diameter; 7. Sealing seat; 71. Cylinder structure. DETAILED DESCRIPTION

[0060] The following will be combined with the drawings in the embodiments of the utility model to clearly and completely describe the technical solutions in the embodiments of the utility model. Obviously, the described embodiments are only part of the embodiments of the utility model, not all of the embodiments. Based on the embodiments in the utility model, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the utility model.

[0061] Medium liquid is: the liquid sucked by the pump when it is working.

[0062] The friction surface includes a gap space between the first friction surface 11 and the second friction surface 21 .

[0063] Embodiment 1:

[0064] Reference Figure 1 - Fig. 9 .

[0065] This embodiment provides a spiral pressurized liquid sealing structure, including a sleeve 51, a gland 52, and a liquid injection hole 53, including:

[0066] The moving ring 1 is fixedly sleeved on the outer side of the shaft sleeve 51 and rotates synchronously with the shaft sleeve 51;

[0067] The stationary ring 2 is connected to the inner wall of the gland 52 and does not rotate with the shaft sleeve 51;

[0068] The shaft sleeve 51 drives the moving ring 1 to rotate relative to the stationary ring 2.

[0069] The dynamic ring 1 and the static ring 2 rub against each other, wherein the friction surface of the dynamic ring 1 is a first friction surface 11;

[0070] The friction surface of the stationary ring 2 is a second friction surface 21;

[0071] The dynamic ring 1 has a flow-disturbing structure 12, and the flow-disturbing structure 12 is arranged around the first friction surface 11 in the radial direction;

[0072] The length direction of the spoiler structure 12 is inclined relative to the adjacent diameter 6 in the opposite direction of the rotation of the moving ring 1;

[0073] The adjacent diameter 6 is: a diameter of the first friction surface 11 passing through the end point of the spoiler structure 12 close to the center of the first friction surface 11;

[0074] The outer wall surface of the moving ring 1 has a flow-guiding thread 14;

[0075] The thread rotation direction of the guide thread 14 is opposite to the rotation direction of the dynamic ring 1, so as to guide the liquid around the dynamic ring 1 along the axis in a direction away from the first friction surface 11;

[0076] The sealing seat 7 is fixedly connected to the gland 52 and sleeved to the outer side of the stationary ring 2. A sealing ring is provided between the sealing seat 7 and the stationary ring 2.

[0077] One end of the sealing seat 7 has a cylindrical structure 71, and the cylindrical structure 71 wraps around the guide thread 14;

[0078] Moreover, the inner diameter of the cylindrical structure 71 is 1.05-1.2 times the outer diameter of the guide thread 14 .

[0079] The working environment of centrifugal pumps varies greatly. For example, the impurity pump for conveying mud has a large number of solid particles, such as sand. When the dynamic ring 1 rotates with the transmission shaft 56, friction is generated between the static ring 2 and the dynamic ring 1. When particles enter the friction surface, they will scratch the friction surface, affecting the sealing of the mechanical seal and causing leakage. At the same time, when the dynamic ring 1 rotates, the first friction surface 11 and the second friction surface 21 will generate heat and need to be cooled. Generally, the medium liquid conveyed by the centrifugal pump can achieve cooling, but if there are a large number of solid particles in the medium liquid, it is necessary to inject coolant through the outside of the centrifugal pump. The coolant not only has the effect of cooling the friction surface, but also has a flushing effect to a certain extent to prevent solid particles from staying in the friction surface. However, the so-called flushing, the flow rate of the coolant in the friction surface is very low, which can basically be regarded as a kind of penetration, so that a liquid film is generated in the friction surface, so there is still a high probability that the particles are stuck in the friction surface, so as to scratch the first friction surface 11 or the second friction surface 21.

[0080] In this regard, in the present application, a spoiler structure 12 is provided in the dynamic ring 1. The spoiler structure 12 can be specifically provided as a protrusion protruding from the outer circular wall surface of the dynamic ring 1 to form a blade-like structure; or a slot is provided on the wall surface of the first friction surface 11, and the end of the slot passes through the outer circular wall surface of the dynamic ring 1.

[0081] The spoiler structure 12 is located on the outside of the friction surface A11. When the spoiler structure 12 rotates with the moving ring 1, the flow rate of the medium liquid around the moving ring 1 will be accelerated and away from the friction surface. At this time, the flow direction of the medium liquid no longer passes through the friction surface. Specifically, the moving ring 1 rotates with the transmission shaft 56. First, the medium liquid in the friction surface will be affected by the centrifugal force and tend to be thrown out quickly to the surroundings. At the same time, the side wall surface of the spoiler structure 12 stirs the medium liquid, so that the flow rate of the liquid outside the friction surface A11 is accelerated, and finally negative pressure is generated (similar to blowing air above the straw of a cup, the faster the flow rate above, the lower the pressure, and the liquid inside the straw will rise). The medium liquid flows around, and the coolant in the friction surface will be sucked around the friction surface. It is conceivable that in theory, when the rotating ring 1 rotates fast enough, a vortex will be generated, and the medium liquid will generate a horizontal vortex around the friction surface A11, while the friction surface A11 and the friction surface B21 located at the center of the vortex will be completely dry (when the injection hole 53 of the coolant is connected to the air). At this time, it is impossible for the medium liquid and any particles to exist in the friction surface (that is, when the flow rate above the straw is fast enough, the air will no longer enter the straw, but water will flow upward from the straw. In this application, the medium liquid can be understood as air, and the cooling liquid can be understood as water in the straw). Of course, in actual situations, the speed of the dynamic ring 1 is difficult to reach the theoretical state, but it can still have a good guiding effect on the medium liquid around the friction surface, so that the medium liquid carries the particles and moves spirally toward the impeller 55, reducing the radial force and thus reducing the possibility of particles entering the friction surface. The pressure of the coolant outlet (i.e., the gap position near the outer wall of the friction surface) is equal to the original pressure of the coolant minus the negative pressure generated by the liquid around the first friction surface 11. A higher outlet pressure can better increase the flow rate of the coolant toward the mechanical seal chamber and improve the flushing effect on the friction surface. The combination of the two effects can greatly ensure that particles cannot enter the friction surface, causing the first friction surface 11 or the second friction surface 21 to be scratched and lose the sealing effect, thereby increasing the overall service life of the equipment.

[0082] At the same time, the length direction of the spoiler structure 12 is inclined in the opposite direction of the rotation of the sleeve 51 .

[0083] For example, when the sleeve 51 rotates clockwise, the length direction of the spoiler structure 12 tilts counterclockwise;

[0084] On the contrary, when the transmission shaft 56 rotates counterclockwise, the length direction of the spoiler structure 12 tilts clockwise;

[0085] When the moving ring 1 rotates, what we need is to throw the medium liquid away from the friction surface. When the inclination direction of the long side of the spoiler structure 12 is the same as the rotation direction of the transmission shaft 56, the medium liquid will enter the friction surface along the spoiler structure 12.

[0086] like Figure 3-Figure 5shown.

[0087] The outer circumferential wall surface of the moving ring 1 has a flow-guiding thread 14;

[0088] The thread rotation direction of the guide thread 14 is opposite to the rotation direction of the dynamic ring 1 , so as to guide the liquid around the dynamic ring 1 along the axis toward a direction away from the first friction surface 11 .

[0089] Since the diameter of the dynamic ring 1 is limited, it cannot generate a good axial attraction force for the liquid like the impeller 55 , and the axial conveying distance of the liquid is very small, making it difficult to directly convey the liquid to the vicinity of the impeller 55 .

[0090] In this regard, the outer cylindrical side wall of the dynamic ring 1 in this embodiment is provided with a guide thread 14, so the dynamic ring 1 can achieve an effect similar to that of an auger during rotation, and transport the liquid along the centerline direction of the transmission shaft 56. The rotation direction of the spiral line of the guide thread 14 determines the direction of the axial component force. When the rotation direction of the thread is the same as that of the transmission shaft 56, the axial component force is the same as the liquid inlet direction of the centrifugal pump. The dynamic ring 1 is located on the opposite side of the impeller 55 relative to the liquid inlet. Therefore, the rotation direction of the guide thread 14 needs to be opposite to the rotation direction of the transmission shaft 56 so that the liquid flows toward the impeller 55.

[0091] When the medium liquid is blocked around the sealing surface by the spoiler groove 13, the guide thread 14 further transports the medium liquid toward the impeller 55, so that the particles have no time and opportunity to enter the friction surface.

[0092] More specifically, the guide thread 14 is not a common thread for fastening, but a trapezoidal thread or a sawtooth thread commonly used for transmission. These two types of threads have a wider pitch and a higher thread tooth, and can push more liquid to flow when rotating. More specifically, the thread pitch is 4mm to 8mm, and the thread tooth height is 1mm to 3mm.

[0093] Furthermore, the sealing seat 7 is fixedly connected to the gland 52 and sleeved to the outer side of the stationary ring 2, and a sealing ring is provided between the sealing seat 7 and the stationary ring 2;

[0094] One end of the sealing seat 7 has a cylindrical structure 71, and the cylindrical structure 71 is wrapped around the guide thread;

[0095] Moreover, the inner diameter of the cylindrical structure 71 is 1.05-1.2 times the outer diameter of the dynamic ring 1 .

[0096] During the operation of the centrifugal pump, the rotation speed of the moving ring 1 is constant, wherein the rotation speed of the guide thread 14 determines the power for discharging particles. It is well known that when the power remains constant, the smaller the diameter of the water outlet, the faster the flow rate, and the farther the distance of the liquid injection. In the prior art, there is only liquid on the periphery of the moving ring 1, that is, when the guide thread 14 transports liquid, it transports the liquid in the entire machine sealing chamber, which is equivalent to a very large water outlet. For this reason, in this embodiment, a cylindrical structure 71 is extended from the end of the sealing seat 7 to wrap the guide thread 14, thereby reducing the water outlet and improving the axial conveying effect of the guide thread 14 on the liquid.

[0097] Specifically, when there is no cylindrical structure 71, the resistance to liquid flow in the radial direction of the guide thread 14 is only hydraulic pressure, which is basically the same as the resistance to liquid flow in the axial direction. Therefore, when the guide thread 14 rotates, a large part of the liquid will diffuse along the diameter direction, especially the end of the guide thread 14 close to the first friction surface 11, which is still close to the friction surface after radial diffusion, and has a general ability to discharge particles.

[0098] In this embodiment, a cylinder structure 71 is added, and when the liquid flows in the radial direction, it will be squeezed by the inner wall surface of the cylinder structure 71, so that the liquid continues to flow along the axial direction of the guide thread 14 until it flows out of the cylinder structure 71. After the liquid flows out of the cylinder structure 71, the distance from the liquid to the friction surface becomes farther, and it is more difficult to enter the friction surface.

[0099] The inner diameter of the cylindrical structure 71 is 1.05-1.2 times the outer diameter of the guide thread 14. When the radial flow distance of the liquid is limited, if the inner diameter of the cylindrical structure 71 is too large, the effect of blocking the radial flow of the liquid will be lost.

[0100] Furthermore, there are multiple spoiler structures 12 arranged in a circular array around the axis of the moving ring 1 .

[0101] Example 2

[0102] like Figure 1-Figure 8 shown.

[0103] The spoiler structure 12 is configured as a spoiler groove 13 recessed in the first friction surface 11;

[0104] The length of the spoiler groove 13 is L1, and the width of the first friction surface 11 is L2;

[0105] L1 <L2;

[0106] The width of the first friction surface 11 is: the distance between the outer circle radius and the inner circle radius of the first friction surface 11;

[0107] The starting end of the spoiler groove 13 in the length direction passes through the outer circumferential wall surface of the moving ring 1;

[0108] The starting end of the spoiler groove 13 in the length direction forms a spoiler area 131;

[0109] The remaining length area forms a guide area 132 to guide the coolant to enter.

[0110] The method of using convexities to form vortices requires the rotating ring 1 to rotate at a higher speed to form a stronger negative pressure. It is well known that the flow rate is inversely proportional to the cross-sectional area of ​​the pipe. The larger the mouth is, the slower the air flow speed we blow out. For the convex form, the cross-sectional area of ​​the pipe is equivalent to the entire annular area between the outer circular wall of the entire rotating ring 1 and the convexity.

[0111] For this purpose, the present application adopts the form of a groove. In Example 1, the contact surface formed by the first friction surface 11 and the second friction surface 21 is originally a complete ring. In this embodiment, the first friction surface 11 is provided with a spoiler groove 13, wherein the length L1 of the spoiler groove 13 is less than the width L2 of the first friction surface 11, and the starting end of the length of the spoiler groove 13 passes through the outer circumferential wall surface of the moving ring 1. At this time, when the moving ring 1 rotates, the end of the spoiler groove 13 is equivalent to the protrusion in Example 1, which is used to stir the medium liquid, so the starting end of the length direction of the spoiler groove 13 forms a spoiler area 131; the remaining length area and the second friction surface 21 form a pipeline to guide the coolant in the friction surface outward through the pipeline, so a guide area 132 is formed.

[0112] In fact, in this embodiment, the shape of the first friction surface 11 is no longer a complete ring, but a cross-section similar to a gear. The area from the end of the spoiler groove 13 to the inner circle of the friction surface is the sealing area.

[0113] When the spoiler groove 13 rotates, the liquid in the guide area 132 will be quickly thrown out to the surroundings due to the centrifugal force, and the liquid in the guide area 132 will not be squeezed by the first friction surface 11 and the second friction surface 21, and the weight is much higher than the mass of the liquid in the friction surface. Therefore, the liquid in the guide area 132 is very easy to flow around, which makes it easier for the pressure in the guide area 132 to drop, and it is easier to attract the coolant to flow out in this direction. As the coolant flows into the guide area 132, the coolant in the guide area 132 will form an annular area around the outside of the sealing area as the spoiler groove 13 rotates, and the wall particles enter the inner friction surface to affect the sealing performance.

[0114] Example 3

[0115] like Figure 1-Figure 8 shown.

[0116] The second friction surface 21 is concave to form a jet groove 22;

[0117] When the spoiler groove 13 rotates with the moving ring 1 and overlaps with the projection of the jet groove 22 toward the first friction surface 11, the spoiler groove 13 and the jet groove 22 form a jet cavity 23;

[0118] The liquid in the jet cavity 23 enters the spoiler groove 13 as the spoiler groove 13 rotates, and is squeezed to form a jet in the diameter direction.

[0119] In the above embodiment, when the spoiler groove 13 contacts the second friction surface 21, since the second friction surface 21 is a plane, the liquid (coolant and medium liquid) inside the spoiler groove 13 is in a stable flow during the rotation of the spoiler groove 13. In order to better rinse the particles, a stronger jet is required.

[0120] Because the orientation and position of the jet groove 22 and the spoiler groove 13 are symmetrical along the above-mentioned friction surface, there is an angle of overlap between the projection of the jet groove 22 and the spoiler groove 13 during the rotation of the dynamic ring 1. When the spoiler groove 13 overlaps with the jet groove 22, a larger cavity will be formed (relative to the spoiler groove 13 and the second friction surface 21). Before the two overlap, the fluidity of the liquid in the jet groove 22 is much lower than that of the liquid in the spoiler groove 13. After the two overlap, the liquids of the two merge into one. As the dynamic ring 1 rotates further, the jet cavity 23 gradually shrinks, and the liquid in the jet cavity 23 will preferentially enter the spoiler groove 13, but the space in the spoiler groove 13 is not enough to accommodate all the liquid in the jet cavity 23. All the liquid will be squeezed, and the squeezed liquid will release pressure toward the low-pressure area, that is, the liquid area around the dynamic ring 1 that is stirred. This process is extremely short in actual situations, and the liquid will quickly burst out to the surroundings, producing a jet effect to flush the friction surface, and make the surrounding medium further away from the friction surface, making it more difficult to enter the friction surface.

[0121] Example 4

[0122] like Figure 1 , Figure 2 shown.

[0123] The outer diameter of the dynamic ring 1 is greater than the outer diameter of the static ring 2 , so that the start end of the spoiler groove 13 in the length direction protrudes from the outer wall surface of the static ring 2 .

[0124] In the sealing structure normally used in centrifugal pumps, the outer diameters of the dynamic ring 1 and the static ring 2 are often equal, and in particular, the outer diameter of the static ring 2 will not be larger than the outer diameter of the dynamic ring 1. This is because the impeller 55 in the centrifugal pump has a balancing hole 551 connecting the mechanical seal chamber and the liquid inlet area, so that the pressure at both ends of the impeller 55 is balanced, so the medium liquid will flow toward the balancing hole 551. If the outer diameter of the dynamic ring 1 is larger than the outer diameter of the static ring 2, a step will be generated to block the flow of the medium liquid, causing particles to accumulate at the step position, increasing the risk of particles entering the friction surface.

[0125] However, in the present application, the first friction surface 11 of the dynamic ring 1 has a spoiler groove 13, and the spoiler groove 13 is occupied by coolant. The outer side of the friction surface is protected by the flowing coolant, and the medium liquid is difficult to enter, and can only flow further around with the coolant. When the outer circular wall surface of the dynamic ring 1 is larger than the outer circular wall surface of the static ring 2, the flow range will be correspondingly increased, so there will be no problem of particle accumulation.

[0126] Moreover, it is well known that the resistance of a cylinder is very small when it rotates along the axis in water, so it is difficult to generate a vortex. In this embodiment, the spoiler structure 12 is a groove body. Although the resistance is increased compared with the complete cylinder, it is still very small compared with the protruding spoiler structure 12. In this regard, in the present application, by increasing the diameter of the dynamic ring 1, a part of the side wall surface of the spoiler groove 13 (a part protruding from the static ring 2) can directly contact the medium liquid, increasing the contact between the dynamic ring 1 and the medium liquid when rotating, thereby increasing the spoiler effect and generating a vortex with greater gravitational force.

[0127] Example 5

[0128] like Figure 2 shown.

[0129] The depth of the spoiler groove 13 is H1;

[0130] Among them, 0.3mm

[0131] The deeper the spoiler groove 13 is, the greater the amount of liquid that can be stirred (along the axial direction), but the resistance will also increase accordingly, and the distance between the point where the friction force is applied and the connection position at the bottom of the spoiler groove 13 will increase accordingly. When the moving ring 1 rotates, the stress on the spoiler groove 13 will be concentrated in large quantities at the connection position. When the depth of the spoiler groove 13 increases, the resistance of the liquid increases, and at the same time, the force arm at the position where the friction force is applied increases, which causes the stress on the connection position to increase exponentially, increasing the possibility of damage and deformation of the spoiler groove 13, and losing the ultimate goal of increasing the service life of the equipment. Especially when there are a large number of spoiler grooves 13, the distance between the spoiler grooves 13 is short, the wall surface is weak, and the structural strength of the spoiler grooves 13 is reduced, making it more prone to damage.​

[0132] Therefore, the depth of the spoiler groove 13 is set between 0.3 mm and 0.6 mm.

[0133] The depth of 0.3 mm is sufficient to draw the liquid in the friction surface outward, and then the liquid around the friction surface is transported toward the impeller 55 through the guide thread 14 on the side wall of the dynamic ring 1.

[0134] Example 6

[0135] like Figure 6 shown.

[0136] The width of the spoiler groove 13 is L1, and the width of the jet groove 22 is L2;

[0137] Among them, 0.5mm <L1=L2<1mm;

[0138] The number of the spoiler grooves 13 is N1, and the number of the jet grooves 22 is N2;

[0139] Among them, 25 <N1<60。

[0140] In Example 5, it is mentioned that when the gap between the spoiler grooves 13 and the spoiler grooves 13 is too small, the spoiler groove 13 structure will become fragile and easy to be damaged. There are two factors that affect the size of the gap between the spoiler grooves 13: 1. The width of the spoiler grooves 13; 2. The number of spoiler grooves 13. At the same time, these two factors are also factors that affect the ease with which the coolant flows out. When the coolant is injected at the same pressure, the wider the spoiler grooves 13 and the more spoiler grooves 13 there are, the easier it is for the coolant to flow out. The more coolant flows out of the friction surface, the coolant flow area formed on the outside of the dynamic ring 1 can better drive the medium liquid to flow in the direction away from the friction surface.

[0141] Example 7

[0142] The dynamic ring 1 and the static ring 2 are made of pressureless sintered silicon carbide. The spiral pressurized liquid sealing structure of this application is mainly used in centrifugal pumps, especially in scenarios where there are many solid particles in the medium liquid, the service life of the mechanical seal is more significantly improved. Therefore, the material of the dynamic ring 1 and the static ring 2 is also selected based on the application scenario with many solid particles. Silicon carbide has the characteristics of corrosion resistance, high temperature resistance, high strength, good thermal conductivity, and impact resistance. Using it to make the dynamic ring 1 and the static ring 2 can greatly improve the service life of the sealing structure.

[0143] Example 8

[0144] like Figure 1-Figure 9 shown.

[0145] The shaft sleeve 51 has a mounting hole 41;

[0146] The axis of the mounting hole 41 is parallel to the axis of the bushing 51;

[0147] A cylindrical transmission pin 42 is fixedly arranged in the mounting hole 41;

[0148] The inner circumferential wall surface of the moving ring 1 has an arc-shaped transmission groove 43;

[0149] The transmission groove 43 is coaxially matched with the transmission pin 42, so that the moving ring 1 rotates synchronously with the bushing 51.

[0150] In the prior art, the axial direction of the transmission pin 42 is parallel to the radial direction of the transmission shaft 56. When the transmission shaft 56 rotates, the bushing 51 is driven through a key and a keyway, and then the bushing 51 drives the moving ring 1 through the transmission pin 42. Actually, the transmission pin 42 acts as a key in this process. The transmission pin 42 is fixedly connected to the outer circumferential wall surface of the bushing 51, and a notch is arranged on the inner circumferential wall surface of the moving ring 1. The length direction of the notch is parallel to the axis direction of the moving ring 1. When the transmission pin 42 rotates, it abuts against one of the side wall surfaces of the notch (the notch presents a U shape when viewed from the end face of the moving ring 1), thereby driving the moving ring 1 to rotate. During the start-up and stop processes of this process, the transmission pin 42 impacts the two side wall surfaces of the notch respectively, which easily damages the moving ring 1. In the prior art, the moving ring 1 is mostly made of cemented carbide material. Compared with silicon carbide, cemented carbide has better toughness and is not easily broken. Therefore, in the actual use process, it will only cause the notch to deform, which has little impact on normal use. And for the cemented carbide material with good toughness, deformation occurs due to the accumulation of long-term collisions. By the time the notch is truly damaged, the first friction surface 11 or the second friction surface 21 has already been damaged and the moving ring 1 and the stationary ring 2 need to be replaced.

[0151] In this application, the service life of the first friction surface 11 and the second friction surface 21 is greatly increased through the flow disturbance structure 12 and the silicon carbide material. Since silicon carbide has poor toughness and deformation and breakage are probabilistic events, it is very likely to break when the first friction surface 11 and the second friction surface 21 are intact.

[0152] Therefore, the transmission groove 43 of the moving ring 1 is set to be arc-shaped. The arc-shaped transmission groove 43 is matched with the cylindrical transmission pin 42, which can avoid stress concentration at the corner of the notch wall surface. And the axes of the transmission pin 42 and the transmission groove 43 are parallel to each other, and the angle between the transmission pin 42 and the transmission groove 43 will not change due to the rotation of the transmission pin 42 with the bushing 51. Therefore, the contact area is much larger than the notch in the prior art (the transmission pin 42 arranged in the radial direction will cause the angle between the two to change due to relative movement with the moving ring 1 and cannot ensure parallelism). Then, the acting force is further dispersed through the arc-shaped wall surface of the transmission groove 43, minimizing the damage to the moving ring 1 caused by the impact.

[0153] Example 10

[0154] A flow component, comprising a spiral pressurized liquid sealing structure as described in any one of the above embodiments, the flow component comprising:

[0155] Pump housing 54;

[0156] An impeller 55 disposed in a pump housing 54;

[0157] A transmission shaft 56 driving the impeller 55 to rotate;

[0158] The shaft sleeve 51 of the spiral pressurized liquid sealing structure is sleeved with the transmission shaft 56;

[0159] A pump cover 57 connected to the pump housing 54 and located on the opposite end surface of the water inlet of the pump housing 54;

[0160] The gland 52 of the spiral pressurized liquid sealing structure is connected to the pump cover 57 .

[0161] In the description of the embodiments of the present invention, it should be understood that the terms "upper", "lower", "front", "back", "left", "right", "vertical", "horizontal", "center", "top", "bottom", "top", "bottom", "inside", "outside", "inner side", "outer side" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present invention. Among them, "inside" refers to an internal or enclosed area or space. "Periphery" refers to the area surrounding a specific component or a specific area.

[0162] In the description of the embodiments of the present utility model, the terms "first", "second", "third", and "fourth" are used for descriptive purposes only and cannot be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features defined as "first", "second", "third", and "fourth" may explicitly or implicitly include one or more of the features. In the description of the present utility model, unless otherwise specified, the meaning of "multiple" is two or more.

[0163] In the description of the embodiments of the present invention, it should be noted that, unless otherwise clearly specified and limited, the terms "install", "connect", "connect", and "assemble" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a direct connection, or an indirect connection through an intermediate medium, or it can be the internal communication of two components. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0164] In the description of the embodiments of the present invention, specific features, structures, materials or characteristics may be combined in a suitable manner in any one or more embodiments or examples.

[0165] In the description of the embodiments of the present utility model, it is necessary to understand that "-" and "~" represent a range of two identical values, and the range includes the endpoints. For example, "AB" represents a range greater than or equal to A and less than or equal to B. "A~B" represents a range greater than or equal to A and less than or equal to B.

[0166] In the description of the embodiments of the present utility model, the term "and / or" is used herein to describe the association relationship of associated objects, indicating that three relationships may exist. For example, A and / or B may represent: A exists alone, A and B exist at the same time, and B exists alone. In addition, the character " / " in this article generally indicates that the associated objects before and after are in an "or" relationship.

[0167] Although the embodiments of the present invention have been shown and described, it will be appreciated by those skilled in the art that various changes, modifications, substitutions and variations may be made to the embodiments without departing from the principles and spirit of the present invention, and that the scope of the present invention is defined by the appended claims and their equivalents.

Claims

1. A spiral pressurized liquid sealing structure, comprising a shaft sleeve, a gland, a liquid injection hole, and a sealing seat, characterized in that: include: A moving ring, fixedly sleeved on the outer side of the shaft sleeve, and rotating synchronously with the shaft sleeve; A stationary ring connected to the inner wall of the gland and not rotating with the shaft sleeve; The shaft sleeve drives the moving ring to rotate relative to the stationary ring; The dynamic ring and the static ring rub against each other, wherein the friction surface of the dynamic ring is a first friction surface; The friction surface of the stationary ring is the second friction surface; Wherein, the dynamic ring has a flow-disturbing structure, and the flow-disturbing structure is arranged around the first friction surface in a radial direction; Wherein, the length direction of the spoiler structure is inclined relative to the adjacent diameter in the opposite direction of the rotation of the moving ring; The adjacent diameter is: a diameter of the first friction surface passing through the end point of the spoiler structure close to the center of the first friction surface; Wherein, the outer circumferential wall surface of the moving ring has a flow-guiding thread; The thread rotation direction of the guide thread is opposite to the rotation direction of the dynamic ring, so as to guide the liquid around the dynamic ring along the axis in a direction away from the first friction surface; The sealing seat is fixedly connected to the gland and sleeved to the outer side of the static ring, and a sealing ring is provided between the sealing seat and the static ring; Wherein, one end of the sealing seat has a cylindrical structure, and the cylindrical structure wraps around the guide thread; Furthermore, the inner diameter of the cylindrical structure is 1.05-1.2 times the outer diameter of the guide thread.

2. A spiral pressurized liquid sealing structure according to claim 1, characterized in that: There are multiple spoiler structures arranged in a circular array around the axis of the moving ring.

3. A spiral pressurized liquid sealing structure according to claim 2, characterized in that: The spoiler structure is configured as a spoiler groove recessed in the first friction surface; The length of the spoiler groove is L1, and the width of the first friction surface is L2; L1 <L2; The width of the first friction surface is: the distance between the outer circle radius and the inner circle radius of the first friction surface; Wherein, the starting end of the spoiler groove in the length direction passes through the outer circular wall surface of the dynamic ring; The starting end of the spoiler groove in the length direction forms a spoiler area; The remaining length area forms a guide area to guide the coolant in.

4. A spiral pressurized liquid sealing structure according to claim 3, characterized in that: The second friction surface is concave to form a jet groove; When the spoiler groove rotates with the moving ring and overlaps with the projection of the jet groove toward the first friction surface, the spoiler groove and the jet groove form a jet cavity; Wherein, the liquid in the jet cavity enters the spoiler groove as the spoiler groove rotates, and is squeezed to form a jet in the diameter direction.

5. A spiral pressurized liquid sealing structure according to claim 4, characterized in that: The outer diameter of the dynamic ring is greater than the outer diameter of the static ring, so that the start end of the spoiler groove in the length direction protrudes from the outer wall surface of the static ring.

6. A spiral pressurized liquid sealing structure according to claim 5, characterized in that: The depth of the spoiler groove is H1; Among them, 0.3mm <H1<0.6mm。 7. A spiral pressurized liquid sealing structure according to claim 6, characterized in that: The width of the spoiler groove is L3; Among them, 0.5mm <L3<1mm; The number of the spoiler grooves is N1; Among them, 25 <N1<60。 8. A spiral pressurized liquid sealing structure according to claim 7, characterized in that: The dynamic ring and the static ring are made of pressureless sintered silicon carbide.

9. A spiral pressurized liquid sealing structure according to claim 8, characterized in that: The shaft sleeve has a mounting hole; The axis of the mounting hole is parallel to the axis of the sleeve; A cylindrical transmission pin is fixedly arranged in the mounting hole; The inner wall surface of the moving ring has an arc-shaped transmission groove; The transmission groove is coaxially matched with the transmission pin so that the movable ring rotates synchronously with the shaft sleeve.

10. A flow component, characterized in that: A spiral pressurized liquid sealing structure according to any one of claims 1 to 9, wherein the flow-through component comprises: Pump housing; An impeller disposed in a pump casing; A transmission shaft driving the impeller to rotate; The shaft sleeve of the spiral pressurized liquid sealing structure is sleeved with the transmission shaft; A pump cover, connected to the pump housing and located on an end surface opposite to the water inlet of the pump housing; The gland of the spiral pressurized liquid sealing structure is connected to the pump cover.

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