Carrier roller of water self-sealing and centrifugal sealing device and mining belt conveyor

Abstract

The invention belongs to the technical field of sealing of carrier rollers for belt conveyors, and particularly relates to a carrier roller of a water self-sealing and centrifugal sealing device and a mining belt conveyor. The carrier roller comprises a carrier roller assembly, the carrier roller assembly comprises a carrier roller shaft and a carrier roller cylinder, and bearing seats and carrier roller bearings are arranged at the two ends of the interior of the carrier roller cylinder; a water self-sealing assembly and a first centrifugal sealing assembly are arranged on the outer side of the carrier roller bearing; a spiral sealing movable ring and a spiral sealing static ring in the water self-sealing assembly jointly form spiral movable sealing to carry out water self-sealing on the carrier roller bearing; a T-shaped sealing ring in the first centrifugal sealing assembly abuts against the inner wall of a centrifugal sealing static ring to form static sealing. By means of the fluid pumping effect of the variable cross-section spiral groove, a sealed medium is gathered in the pressure gathering groove to dynamically seal the carrier roller bearing, and meanwhile static sealing of the carrier roller assembly is achieved through the first centrifugal sealing assembly and the second centrifugal sealing assembly; sealing of the carrier roller assembly under different working conditions is achieved through combined sealing of the two structures.

Description

Technical Field

[0001] This invention belongs to the field of sealing technology for belt conveyor idlers, specifically relating to an idler with a water self-sealing and centrifugal sealing device and a mining belt conveyor. Background Technology

[0002] Belt conveyors are widely used in industries such as coal mining, power, ports and metallurgy due to their continuous and efficient transportation capabilities. As a key support component, the performance of idler rollers directly affects the system's operating efficiency and stability. Among them, mining belt conveyors, as the core equipment for coal mining and transportation, operate under extreme conditions of high dust, high humidity and even water immersion for a long time, which places higher demands on the sealing performance of idler roller bearings.

[0003] Most existing idler rollers use labyrinth seals, which can provide a good seal against high humidity and high dust in most cases. However, once the idler roller enters a water accumulation condition, whether the idler roller is in a stationary state or in a rotating state during operation, external water can easily mix with the grease in the existing labyrinth seal and damage the labyrinth seal. This allows water from the external environment to enter the idler roller bearing, causing lubrication failure of the idler roller bearing and ultimately leading to the scrapping of the idler roller.

[0004] Currently, a small portion of idlers use contact-type rubber and plastic seals, relying on the elastic lip of the seal to tightly adhere to the idler shaft surface for sealing. While this sealing solution initially provides strong sealing capabilities, the continuous contact between the seal and the shaft significantly increases frictional torque, leading to a marked increase in energy consumption of the transmission system. More importantly, frictional wear between the rubber and plastic seal and the idler shaft is inevitable, causing the sealing contact force to gradually decrease. Seal failure can allow moisture and dust to enter the bearing, rendering the idler unusable. If damaged idlers are not replaced promptly, it can cause the conveyor belt to break or even completely stop the conveyor, resulting in high maintenance costs and significant safety hazards for the safe and stable operation of the conveyor. Summary of the Invention

[0005] The purpose of this invention is to provide a water-sealed and centrifugal sealing device for idlers and mining belt conveyors, which can achieve long-term stable dynamic and static sealing under various complex working conditions such as high dust, high humidity and water immersion, thereby effectively extending the service life of idlers and belt conveyors.

[0006] The technical solution of the present invention is: a water self-sealing and centrifugal sealing device for a roller, including a roller assembly, wherein a water self-sealing component and a first centrifugal sealing component are provided on both the left and right sides of the roller assembly;

[0007] The idler assembly includes an idler shaft, an idler cylinder is sleeved on the outside of the idler shaft, bearing seats are provided at both ends of the inner side of the idler cylinder, an idler bearing is provided between each bearing seat and the idler shaft, and a water self-sealing component and a first centrifugal sealing component are provided on the outside of each idler bearing.

[0008] Two water-sealing assemblies are respectively located on one side of the two idler roller bearings, and the two water-sealing assemblies are symmetrically arranged on the left and right sides of the idler roller assembly. Each water-sealing assembly includes a spiral sealing moving ring and a spiral sealing stationary ring. The spiral sealing moving ring is connected to the bearing housing through a spiral sealing cap. A pressure-gathering groove is opened in the middle of the outer diameter of the spiral sealing moving ring, and several variable cross-section spiral grooves are symmetrically opened on both sides of the pressure-gathering groove. The width and depth of the variable cross-section spiral grooves gradually decrease from the outside to the inside. The spiral sealing stationary ring is sleeved on the idler roller shaft, and one end of the spiral sealing stationary ring extends between the spiral sealing moving ring and the spiral sealing cap. The spiral sealing moving ring and the spiral sealing stationary ring together form a spiral dynamic seal to water-seale the idler roller bearing.

[0009] Two first centrifugal sealing assemblies are respectively located on one side of two water self-sealing assemblies, and the two first centrifugal sealing assemblies are symmetrically located at the left and right ends of the idler roller assembly. Each first centrifugal sealing assembly includes a centrifugal sealing moving ring and a centrifugal sealing stationary ring. One side of the centrifugal sealing moving ring is connected to the inner wall of the bearing seat, and the centrifugal sealing stationary ring is sleeved on the idler roller shaft. One side of the centrifugal sealing stationary ring and one side of the centrifugal sealing moving ring together form a static sealing cavity. A hollow centrifugal sleeve is provided inside the static sealing cavity. A T-shaped sealing ring is provided inside the centrifugal sleeve. The T-shaped sealing ring includes a sealing part and an abutting part. The sealing part extends to the outside of the centrifugal sleeve and abuts against the inner wall of the centrifugal sealing stationary ring. A first pre-tightening spring is provided on the inner diameter side of the abutting part and is connected to the inner wall of the centrifugal sleeve. Several centrifugal rotating mechanisms are symmetrically arranged on both sides of the abutting part. Under the action of centrifugal force, the sealing part of the T-shaped sealing ring is pressed into the interior of the centrifugal sleeve by the centrifugal rotating mechanisms.

[0010] Preferably, the spiral sealing cap has an L-shaped cross-section and includes an integrally formed cap side plate and a cap sleeve with a stepped inner wall. A first static sealing ring is provided between the outer wall of the cap side plate and the centrifugal sealing moving ring, and the first static sealing ring is embedded in the side wall of the cap side plate. A spiral sealing ring is provided at the stepped inner wall of the cap sleeve. One end of the spiral sealing ring has a positioning protrusion, which is located between the outer ring of the idler roller bearing and the cap sleeve. The other end of the spiral sealing ring and the stepped side wall of the cap sleeve together form a T-shaped cavity. A second centrifugal sealing assembly is installed in the T-shaped cavity. The second centrifugal sealing assembly includes a second pre-tightening spring connected to the inner wall of the cap sleeve. One end of the second pre-tightening spring is connected to a sealing retaining ring. One end of the sealing retaining ring abuts against the outer wall of the spiral sealing static ring, and the axial sides of the sealing retaining ring are limited by the cap sleeve and the spiral sealing ring, respectively.

[0011] Preferably, the spiral sealing stationary ring has an L-shaped cross-section and includes an integrally formed spiral stationary ring sleeve and a spiral stationary ring side plate. The spiral stationary ring sleeve is located between the spiral sealing pressure ring and the spiral sealing moving ring. Several annular grooves are formed on the outer wall of the spiral stationary ring sleeve. The spiral stationary ring side plate is sleeved on the idler roller shaft. The inner diameter of the spiral stationary ring side plate is provided with a spiral stationary ring positioning part that abuts against the inner ring of the idler roller bearing. One side of the idler roller bearing is provided with a first positioning groove for installing a bearing retaining ring, and a bearing washer is provided between this side of the idler roller bearing and the corresponding bearing seat side wall. One side of the spiral stationary ring positioning part is provided with a second positioning groove for installing an elastic retaining ring. Both the first positioning groove and the second positioning groove are formed on the idler roller shaft. A second stationary sealing ring is provided between the spiral stationary ring positioning part and the idler roller shaft.

[0012] Preferably, the spiral sealing ring is bolted to the gland side plate. A spiral sealing ring positioning part is provided on one side of the spiral sealing ring, and the side wall of the positioning part abuts against the inner wall of the gland side plate. A third static sealing ring is provided between the positioning part and the inner wall of the gland side plate. Several equal-section spiral grooves are evenly distributed on the inner wall of the spiral sealing ring. When the rotation direction of the idler roller cylinder is clockwise when viewed from the right side of the idler roller, several equal-section spiral grooves on the spiral sealing ring on the right side of the idler roller assembly are left-handed spiral grooves. On the spiral sealing ring on the right side of the idler roller assembly, the rotation direction of the variable-section spiral groove to the left of the pressure-gathering groove is the same as the rotation direction of its corresponding equal-section spiral groove. Several equal-section spiral grooves on the spiral sealing ring on the left side of the idler roller assembly are right-handed spiral grooves. On the spiral sealing ring, the spiral direction of the variable cross-section spiral groove on the right side of the pressure-gathering groove is the same as the spiral direction of its corresponding constant cross-section spiral groove. When the rotation direction of the idler roller body is counterclockwise when viewed from the right side of the idler roller, several constant cross-section spiral grooves on the spiral sealing ring on the right side of the idler roller assembly are all right-hand spiral grooves. On this spiral sealing ring, the spiral direction of the variable cross-section spiral groove on the left side of the pressure-gathering groove is the same as the spiral direction of its corresponding constant cross-section spiral groove. Several constant cross-section spiral grooves on the spiral sealing ring on the left side of the idler roller assembly are all left-hand spiral grooves. On the spiral sealing ring on the left side of the idler roller assembly, the spiral direction of the variable cross-section spiral groove on the right side of the pressure-gathering groove is the same as the spiral direction of its corresponding constant cross-section spiral groove. Gaps are provided between the spiral sealing ring and the idler roller shaft, between the spiral sealing ring and the spiral sealing stationary ring, and between the spiral sealing stationary ring and the spiral sealing pressure ring.

[0013] Preferably, the ratio between the outer groove width and the inner groove width of the variable cross-section spiral groove ranges from 1 to 3, the ratio between the outer groove depth and the inner groove depth ranges from 1 to 3, and the spiral angle of the variable cross-section spiral groove is 10 to 30°; when the inner groove width and inner groove depth of the variable cross-section spiral groove are constant, the formula for the total sealing pressure P under different outer groove widths A, different outer groove depths B, and different spiral angles β is: P = 148.1 - 17.45 × A + 17.84 × B - 58.95 × β - 89.35 × AB - 43.3 × Aβ - 37.05 × Bβ + 60.87 × A 2 +61.22×B 2 +78.85×β 2 ; The unit of the total sealing pressure P is kPa.

[0014] Preferably, the centrifugal sealing ring has a U-shaped cross-section and includes an integrally formed centrifugal sealing ring outer sleeve, a connecting part, and a centrifugal sealing ring inner sleeve. A fourth static sealing ring is provided between the centrifugal sealing ring outer sleeve and the bearing seat, and the fourth static sealing ring is embedded in the outer wall of the centrifugal sealing ring outer sleeve. One end of the centrifugal sealing ring outer sleeve abuts against the side wall of the spiral sealing cover. The centrifugal sealing ring outer sleeve and the centrifugal sealing ring inner sleeve are connected by the connecting part. A third positioning groove for installing an elastic retaining ring is provided on one side of the connecting part. The third positioning groove is opened on the inner wall of the bearing seat. The centrifugal sealing ring inner sleeve is sleeved on the outside of the idler roller shaft, and a gap is provided between the centrifugal sealing ring inner sleeve and the idler roller shaft.

[0015] Preferably, the centrifugal sealing stationary ring has an L-shaped cross-section and includes an integrally formed centrifugal stationary ring sleeve and a centrifugal stationary ring side plate. The centrifugal stationary ring sleeve is located between the outer sleeve of the centrifugal moving ring and the inner sleeve of the centrifugal moving ring. The centrifugal stationary ring side plate is sleeved on the idler roller shaft. A centrifugal stationary ring positioning part is provided at the inner diameter of the centrifugal stationary ring side plate. A fifth stationary sealing ring is provided between the inner diameter side of the centrifugal stationary ring positioning part and the idler roller shaft. One side of the centrifugal stationary ring positioning part abuts against the shoulder of the idler roller shaft. A fourth positioning groove for installing an elastic retaining ring is provided on the other side of the centrifugal stationary ring positioning part. The fourth positioning groove is opened on the idler roller shaft.

[0016] Preferably, the centrifugal sleeve is disposed between the outer sleeve of the centrifugal rotating ring and the inner sleeve of the centrifugal rotating ring. The centrifugal sleeve includes an outer ring, an inner ring, and a mounting ring. The mounting ring is sleeved on the inner sleeve of the centrifugal rotating ring. The outer ring and the inner ring are respectively disposed on both sides of the mounting ring. The outer ring abuts against the side wall of the connecting part. One side of the inner ring is provided with a fifth positioning groove for installing the elastic retaining ring. The fifth positioning groove is opened on the side wall of the inner sleeve of the centrifugal rotating ring. A sliding opening is provided between the inner ring and the outer ring. The sealing part of the T-shaped sealing ring extends to the outside of the centrifugal sleeve through the sliding opening and abuts against the inner wall of the centrifugal stationary ring sleeve. The T-shaped sealing ring is composed of several sealing ring segments connected end to end. Each sealing ring segment has a locking part at both ends, and the locking parts at both ends of each sealing ring segment are staggered. There is a gap between two adjacent sealing ring segments.

[0017] Preferably, several centrifugal rotating mechanisms are evenly arranged on both sides of the T-shaped sealing ring. Each centrifugal rotating mechanism includes a mounting base installed inside the centrifugal sleeve. A centrifugal block is rotatably connected to the mounting base via a pin. The centrifugal block has a centrifugal part and a contact part at both ends. The weight of the centrifugal part is greater than the weight of the contact part. The contact part cooperates with the groove on the abutment part.

[0018] A mining belt conveyor includes idlers with the aforementioned water self-sealing and centrifugal sealing devices, and the mining belt conveyor further includes:

[0019] The belt conveyor body includes a drive roller and a driven roller. The drive roller is connected to a power component, which provides rotational power to the drive roller. The drive roller and the driven roller are connected to a conveyor belt and rotate together. The drive roller and the driven roller are respectively located at both ends of the conveyor belt.

[0020] Several idler modules are evenly distributed on the belt conveyor body via support frames, and the idler modules are located between the drive drum and the driven drum. Each idler module includes three sets of idler assemblies located above the support frame and one set of idler assemblies located below the support frame. Above the support frame, the three sets of idler assemblies form a U-shaped idler trough, which is used to support the conveyor belt. The idler assemblies below the support frame work together with the idler assemblies above the support frame to move the conveyor belt.

[0021] The beneficial effects of this invention are as follows: By opening a variable cross-section spiral groove on the spiral sealing ring in the water self-sealing assembly, the fluid pumping effect generated by the variable cross-section spiral groove facing the inner shaft during rotation causes the sealed medium to accumulate inside the pressure-gathering groove along the variable cross-section spiral groove, and the sealing pressure formed inside the variable cross-section spiral groove and the pressure-gathering groove dynamically seals the external water; when the sealed medium is dust, the dust is sealed by the grease added in the annular groove; at the same time, the first centrifugal sealing assembly achieves static sealing of the idler assembly. The T-shaped sealing ring in the first centrifugal sealing assembly is pressed against the inner wall of the centrifugal static sealing ring under the action of the first pre-tightening spring, preventing the external sealed medium from entering the interior of the idler assembly when the idler is stationary, thus avoiding affecting the normal operation of the idler bearing; the combination of the two structures achieves sealing of the idler under different working conditions, and the sealing is reliable, extending the working life of the idler and greatly improving the economic benefits of the mining belt conveyor. Attached Figure Description

[0022] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0023] Figure 1 This is a cross-sectional view of the idler roller assembly in this invention;

[0024] Figure 2 This is a cross-sectional view of the specific structure of the water self-sealing component and the first centrifugal sealing component in this invention;

[0025] Figure 3 This is a schematic diagram of the overall structure of the water self-sealing component in this invention;

[0026] Figure 4 This is a cross-sectional schematic diagram of the water self-sealing component in this invention;

[0027] Figure 5 This is a front view of the spiral sealing ring in this invention;

[0028] Figure 6 This is a schematic diagram of the spiral sealing ring in this invention;

[0029] Figure 7 This is a schematic diagram showing the unfolded cross-section spiral groove in this invention;

[0030] Figure 8 This is a schematic diagram of the mesh division of the variable cross-section spiral groove structure according to the present invention;

[0031] Figure 9 This is a partially enlarged schematic diagram of the mesh division of the variable cross-section spiral groove structure according to the present invention;

[0032] Figure 10 A comparison diagram of the sealing pressure of helical grooves with constant cross-section and helical grooves with variable cross-section at different rotation speeds;

[0033] Figure 11 A comparison chart of sealing pressures of variable cross-section spiral grooves when the outer groove width of the variable cross-section spiral groove is taken as the research variable;

[0034] Figure 12 A comparison chart of sealing pressures of variable cross-section spiral grooves when the outer groove depth is taken as the research variable;

[0035] Figure 13 A comparison chart of sealing pressure of variable cross-section spiral grooves when the helix angle of the variable cross-section spiral groove is the research variable;

[0036] Figure 14This is a cross-sectional schematic diagram of the sealing state of the second centrifugal sealing assembly in this invention;

[0037] Figure 15 This is a cross-sectional schematic diagram showing the second centrifugal sealing gap formed by the second centrifugal sealing assembly in this invention.

[0038] Figure 16 This is a cross-sectional schematic diagram of the sealing state of the first centrifugal sealing assembly in this invention;

[0039] Figure 17 This is a cross-sectional schematic diagram of the first centrifugal sealing assembly in the open state in this invention;

[0040] Figure 18 This is a schematic diagram of the centrifugal sealing ring in this invention;

[0041] Figure 19 This is a cross-sectional schematic diagram of the centrifugal sleeve in this invention;

[0042] Figure 20 This is a schematic diagram of the centrifugal rotation mechanism in this invention;

[0043] Figure 21 This is a schematic diagram of the T-shaped sealing ring in this invention;

[0044] Figure 22 This is a schematic diagram of the leakage path in the static state of the present invention;

[0045] Figure 23 This is a schematic diagram of the leakage path when the sealed medium is a liquid in this invention;

[0046] Figure 24 This is a schematic diagram of the leakage path when the sealed medium is dust in this invention;

[0047] Figure 25 This is a partial structural schematic diagram of the belt conveyor in this invention;

[0048] Figure 26 This is a partial structural diagram of the idler roller module in this invention.

[0049] In the diagram: Idler assembly 1, Idler shaft 11, First positioning groove 11-1, Second positioning groove 11-2, Fourth positioning groove 11-3, Idler cylinder 12, Bearing seat 13, First static seal ring 13-1, Fourth static seal ring 13-2, Third positioning groove 13-3, Idler bearing 14, Bearing washer 15; Water self-sealing assembly 2, Spiral sealing ring 21, Pressure-gathering groove 21-1, Variable cross-section spiral groove 21-2, Spiral ring positioning part 21-3 21-4 (third static sealing ring), 21-5 (equal cross-section spiral groove), 22 (spiral sealing static ring), 22-1 (spiral static ring sleeve), 22-2 (spiral static ring side plate), 22-3 (annular groove), 22-4 (spiral static ring positioning part), 22-5 (second static sealing ring), 23 (spiral sealing gland), 23-1 (gland sleeve), 23-2 (gland side plate), 24 (spiral sealing pressure ring), 24-1 (positioning convex ring), 24-2 (T-shaped cavity); 3. First centrifugal sealing assembly, centrifugal... 31. Seal ring 31, centrifugal ring outer sleeve 31-1, connecting part 31-2, centrifugal ring inner sleeve 31-3, centrifugal sealing ring 32, centrifugal ring sleeve 32-1, centrifugal ring side plate 32-2, centrifugal ring positioning part 32-3, fifth static sealing ring 32-4, static sealing cavity 33, centrifugal sleeve 34, fifth positioning groove 34-1, outer ring 34-2, inner ring 34-3, mounting ring 34-4, T-shaped sealing ring 35, sealing ring. Sealing part 35-1, abutting part 35-2, engaging part 35-3, centrifugal rotating mechanism 36, mounting base 36-1, centrifugal block 36-2, centrifugal part 36-3, contact part 36-4, first pre-tightening spring 37, first centrifugal sealing gap 38; second centrifugal sealing assembly 4, second pre-tightening spring 41, sealing retaining ring 42, second centrifugal sealing gap 43; belt conveyor body 5, driving drum 51, driven drum 52, conveyor belt 53. Detailed Implementation

[0050] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0051] In the description of this invention, it should be noted that the terms "middle," "upper," "lower," "side," "end," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing the invention and for simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on the invention. The terms "first," "second," and "third" are used for descriptive purposes only and should not be construed as indicating or implying relative importance. Furthermore, unless otherwise explicitly specified and limited, the terms "installation," "setting," and "connection" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0052] like Figure 1-22 As shown, a water-sealed and centrifugal sealing device is provided for an idler roller. The idler roller includes an idler roller assembly 1, and water-sealed components 2 and first centrifugal sealing components 3 are provided on both the left and right sides of the idler roller assembly 1. The idler roller assembly 1 includes an idler roller shaft 11, and an idler roller cylinder 12 is sleeved on the outside of the idler roller shaft 11. Bearing seats 13 are provided at both ends of the inner side of the idler roller cylinder 12. An idler roller bearing 14 is provided between each bearing seat 13 and the idler roller shaft 11. A bearing washer 15 is provided between each idler roller bearing 14 and the side wall of its corresponding bearing seat 13. The axial positioning of the outer ring of the idler roller bearing 14 is achieved by the bearing washer 15.

[0053] In this embodiment, as Figure 2-6 As shown, two water-sealing assemblies 2 are respectively located on the outer sides of the two idler roller bearings 14, and the two water-sealing assemblies 2 are symmetrically arranged on the left and right sides of the idler roller assembly 1. Each water-sealing assembly 2 includes a spiral sealing moving ring 21 and a spiral sealing stationary ring 22. The spiral sealing moving ring 21 is connected to the bearing seat 13 through a spiral sealing cap 23. A pressure-gathering groove 21-1 is opened in the middle of the outer diameter of the spiral sealing moving ring 21. Several variable cross-section spiral grooves 21-2 are symmetrically opened on both sides of the pressure-gathering groove 21-1. The groove width and depth of the variable cross-section spiral groove 21-2 gradually decrease from the outside to the inside. The ratio between the outer groove width and the inner groove width of the variable cross-section spiral groove 21-2 ranges from 1 to 3, the ratio between the outer groove depth and the inner groove depth of the variable cross-section spiral groove 21-2 also ranges from 1 to 3, and the helix angle of the variable cross-section spiral groove 21-2 is 10 to 30°. When the inner groove width and inner groove depth of the variable cross-section spiral groove 21-2 are constant, the formula for the total sealing pressure P under different outer groove widths A, different outer groove depths B, and different helix angles β is: P = 148.1 - 17.45 × A + 17.84 × B - 58.95 × β - 89.35 × AB - 43.3 × Aβ - 37.05 × Bβ + 60.87 × A 2 +61.22×B 2 +78.85×β 2 ; The unit of the total sealing pressure P is kPa; the spiral seal stationary ring 22 is sleeved on the idler roller shaft 11, and one end of the spiral seal stationary ring 22 extends between the spiral seal moving ring 21 and the spiral seal cover 23. The spiral seal moving ring 21 and the spiral seal stationary ring 22 together form a spiral dynamic seal to self-seal the idler roller bearing 14.

[0054] By creating a pressure-collecting groove 21-1 in the middle of the outer side of the spiral sealing ring 21, and creating variable cross-section spiral grooves 21-2 on both sides of the pressure-collecting groove 21-1, the variable cross-section spiral grooves 21-2 pump water, drawing the sealed external water into the pressure-collecting groove 21-1 to form a local high-pressure liquid ring, thus achieving the sealing effect on the sealed water. Compared to a constant cross-section spiral groove, the variable cross-section spiral groove 21-2 can further improve the pumping effect of the spiral groove on water, thereby improving the dynamic sealing effect on the idler roller assembly 1.

[0055] The following application will utilize the influence of the groove depth, groove width, and helix angle of the aforementioned spiral groove on the sealing pressure to construct a finite element simulation model, such as... Figure 5-9 As shown, in Figure 5 In the middle, D o L is the outer diameter of the variable cross-section spiral groove 21-2, X is the length of the variable cross-section spiral groove 21-2, Y is the width of the compression groove 21-1, and Y is the depth of the compression groove 21-1; in addition, Figure 7 This is a schematic diagram of the variable cross-section spiral groove 21-2 of this application. In I, a is the inner groove width of the variable cross-section spiral groove 21-2, A is the outer groove width of the variable cross-section spiral groove 21-2, and β is the spiral angle of the variable cross-section spiral groove 21-2. In II, b is the inner groove depth of the variable cross-section spiral groove 21-2, and in III, B is the outer groove depth of the variable cross-section spiral groove 21-2. This application will compare the sealing pressure of the spiral groove in both the constant cross-section spiral groove and the variable cross-section spiral groove structures using the formula obtained from the above influencing factors. The relationship between the above factors and the sealing pressure of the variable cross-section spiral groove 21-2 will be obtained, and then the relationship between the groove depth, groove width, and spiral angle of the variable cross-section spiral groove 21-2 as a whole and the total sealing pressure will be obtained.

[0056] S1. Geometric Model Establishment

[0057] A three-dimensional fluid domain computational model of the spiral seal dynamic ring 21 was established using the CREO modeling software, and numerical simulations were performed on the fluid domain computational model. The design parameters in the model are as follows:

[0058] Design parameters numerical values <![CDATA[Outer diameter of spiral groove (D o ) / mm]]> 80 Spiral groove length (L) / mm 15 Spiral groove sealing gap (c) / mm 0.1 Compression groove width (X) / mm 5 Polymer groove depth (Y) / mm 3 Inner spiral groove width (a) / mm 1 Inner spiral groove depth (b) / mm 1 Outer spiral groove width (A) / mm 1 / 1.5 / 2 / 2.5 / 3 outer spiral groove depth (B) / mm 1 / 1.5 / 2 / 2.5 / 3 Helix angle (β) / ° 10 / 15 / 20 / 25 / 30

[0059] S2, Grid division

[0060] The mesh was generated using Workbench's automatic meshing function, with a mesh size of 0.25 mm. To ensure the accuracy of the simulation results, an "expansion" method was used to add an expansion layer to the static walls of the model, and localized mesh refinement was applied to the walls, such as... Figure 8 and Figure 9 As shown.

[0061] S3, Fluid Finite Element Simulation

[0062] The flow field of the spiral groove and the corresponding sealing gap was simulated using the finite element software Fluent. The mesh model was imported and the turbulence model was selected. In the spiral seal moving ring model, the two sides of the variable cross-section spiral groove were set as pressure inlets, and the pressure was set to atmospheric pressure of 101 kPa. The inner side of the sealed medium was a rotating wall surface with a rotation speed of 1500 r / min. The outer side of the sealed medium was a stationary wall surface and was set to be stationary. It should be noted that in this embodiment, the inner side of the sealed medium is in contact with the spiral seal moving ring 21 and rotates with the spiral seal moving ring 21. Therefore, the inner side of the sealed medium is a rotating wall surface. The outer side of the sealed medium is in contact with the spiral seal stationary ring 22. The spiral seal stationary ring 22 is in a stationary state. Therefore, the outer side of the sealed medium is a stationary wall surface.

[0063] S31. Verify the sealing pressure of the constant cross-section spiral groove and the variable cross-section spiral groove 21-2.

[0064] Simulations were performed using helical grooves with uniform cross-sections of 1×1mm and 3×3mm, respectively. Simultaneously, a helical groove 21-2 with a variable cross-section (inner cross-section 1×1mm, outer cross-section 1×3mm) was created. The sealing pressures of the uniform and variable cross-section helical grooves 21-2 were compared at the same rotational speed. Figure 10 As shown.

[0065] S32. Verify the sealing pressure of the variable cross-section spiral groove 21-2 with different cross-sections.

[0066] With other parameters remaining constant, using a helical groove with a cross-sectional area of ​​1×1mm as the initial parameter, and changing the outer groove width of the helical groove, the following results are obtained. Figure 11 The sealing pressure comparison diagram is shown; by changing the outer groove depth of the spiral groove, the following results are obtained. Figure 12 The sealing pressure comparison chart is shown below;

[0067] Meanwhile, with other parameters remaining constant, the inner cross-section of the spiral groove is 1×1mm, and the outer cross-section is 3×3mm. By changing the spiral angle of the spiral groove, the following results are obtained. Figure 13 The diagram shows a comparison of sealing pressures.

[0068] ① Based on the above simulation process, such as Figure 10 As shown, at the same rotational speed, the sealing pressure of the variable cross-section spiral groove 21-2 is much greater than that of the constant cross-section spiral groove, that is, the sealing strength of the variable cross-section spiral groove 21-2 is greater than that of the constant cross-section spiral groove.

[0069] ② Based on the above simulation process, with the inner groove depth and width of the spiral groove fixed, and the outer groove depth and helix angle remaining unchanged, only the outer groove width of the spiral groove can be changed to obtain the sealing pressure value of the spiral groove at different outer groove widths. After fitting, the sealing pressure P1 of the variable cross-section spiral groove 21-2 under different outer groove widths A is obtained as: P1 = -16.87A + 352.2, where the unit of sealing pressure P1 is kPa; Figure 11 As shown.

[0070] ③ Based on the above simulation process, with the inner groove depth and width of the spiral groove fixed, and the outer groove width and helix angle unchanged, only the outer groove depth of the spiral groove can be changed to obtain the sealing pressure value of the spiral groove at different outer groove depths. After fitting, the sealing pressure P2 of the variable cross-section spiral groove 21-2 at different outer groove depths B is obtained as: P2 = 40.33B + 296.5, and the unit of sealing pressure P2 is kPa; Figure 12 As shown.

[0071] ④ Based on the above simulation process, with the inner groove depth and width of the spiral groove fixed, and the outer groove width and depth remaining unchanged, by only changing the spiral angle, the sealing pressure value P3 of the spiral groove at different spiral angles can be obtained as: P3 = 558.7e -0.0329β Where e is the base of the natural logarithm function, approximately equal to 2.71828, and the unit of sealing pressure P3 is kPa; For example Figure 13 As shown.

[0072] ⑤ Based on the above simulation process, with the inner groove depth and width of the spiral groove fixed, by changing the outer groove depth, outer groove width, and spiral angle, the sealing pressure values ​​of the variable cross-section spiral groove with different outer groove depths, outer groove widths, and spiral angles can be obtained. After fitting, the total sealing pressure P of the variable cross-section spiral groove 21-2 under different outer groove widths A, outer groove depths B, and spiral angles β is obtained as follows: P = 148.1 - 17.45 × A + 17.84 × B - 58.95 × β - 89.35 × AB - 43.3 × Aβ - 37.05 × Bβ + 60.87 × A 2 +61.22×B 2 +78.85×β 2 ; The unit of the total sealing pressure P is kPa.

[0073] In this embodiment, as Figure 2-4 and Figure 14 , Figure 15 As shown, the spiral sealing cap 23 has an L-shaped cross-section. The spiral sealing cap 23 includes an integrally formed cap side plate 23-2 and a cap sleeve 23-1 with a stepped inner wall. A first static sealing ring 13-1 is provided between the outer wall of the cap side plate 23-2 and the centrifugal sealing ring 31. The first static sealing ring 13-1 is embedded in the side wall of the cap side plate 23-2. Since the spiral sealing cap 23 and the centrifugal sealing ring 31 remain relatively stationary, the first static sealing ring 13-1 provides a static seal between the spiral sealing cap 23 and the centrifugal sealing ring 31. The inner wall of the cap sleeve 23-1 has a stepped section... A spiral sealing ring 24 is provided, one end of which has a positioning protrusion 24-1. The positioning protrusion 24-1 is positioned between the outer ring of the idler roller bearing 14 and the pressure sleeve 23-1. The two sides of the positioning protrusion 24-1 abut against the outer ring of the idler roller bearing 14 and the end of the pressure sleeve 23-1, respectively, thereby axially positioning the spiral sealing ring 24 and the pressure sleeve 23-1. The other end of the spiral sealing ring 24 and the side wall of the step of the pressure sleeve 23-1 together form a T-shaped cavity 24-2. A second centrifugal sealing assembly 4 is installed in the T-shaped cavity 24-2. The second centrifugal sealing assembly 4 includes a second preload spring 41 connected to the inner wall of the pressure sleeve 23-1. One end of the second preload spring 41 is connected to a sealing retaining ring 42. One end of the sealing retaining ring 42 abuts against the outer wall of the spiral sealing stationary ring 22, and the axial sides of the sealing retaining ring 42 are respectively limited by the pressure sleeve 23-1 and the spiral sealing pressure ring 24. It should be noted that when the idler roller cylinder 12 is stationary, one end of the sealing retaining ring 42 abuts against the outer wall of the spiral sealing stationary ring 22 through the preload force of the second preload spring 41, thereby achieving a static seal for the idler roller assembly 1. When the idler roller cylinder 12 rotates, Under the action of centrifugal force, the sealing retaining ring 42 compresses the second pre-tightening spring 41 and separates from the spiral sealing stationary ring 22, ensuring that the roller cylinder 12 drives the spiral sealing ring 21 to rotate through the spiral sealing cover 23. The outer wall of the sealing retaining ring 42 and the spiral sealing stationary ring 22 forms a gap to prevent contact and wear. The sealing retaining ring 42 is a segmented design, consisting of several ring segments connected end to end to form the sealing retaining ring 42. Each ring segment has an extension at both ends, and the extensions at both ends of each ring segment are staggered. There is a gap between two adjacent ring segments to ensure that the sealing retaining ring 42 can be completely pressed into the interior of the T-shaped cavity 24-2.

[0074] Specifically, such as Figure 1-4As shown, the spiral sealing stationary ring 22 has an L-shaped cross-section. The spiral sealing stationary ring 22 includes an integrally formed spiral stationary ring sleeve 22-1 and a spiral stationary ring side plate 22-2. The spiral stationary ring sleeve 22-1 is located between the spiral sealing pressure ring 24 and the spiral sealing moving ring 21. Several annular grooves 22-3 are formed on the outer wall of the spiral stationary ring sleeve 22-1. Specifically, in this embodiment, grease can be added into the annular grooves 22-3 to seal against external dust in the absence of water accumulation. The spiral stationary ring side plate 22-2 is sleeved on the idler roller shaft 11, and its inner diameter is provided with a connection to the idler roller bearing. The inner ring of the roller bearing 14 abuts against the spiral stationary ring positioning part 22-4. One side of the roller bearing 14 is provided with a first positioning groove 11-1 for installing the bearing retaining ring, and one side of the spiral stationary ring positioning part 22-4 is provided with a second positioning groove 11-2 for installing the elastic retaining ring. Both the first positioning groove 11-1 and the second positioning groove 11-2 are opened on the roller shaft 11. A second static sealing ring 22-5 is provided between the spiral stationary ring positioning part 22-4 and the roller shaft 11. The static seal between the spiral sealing stationary ring 22 and the roller shaft 11 is achieved by the second static sealing ring 22-5, preventing the external sealed medium from entering the interior of the roller assembly 1.

[0075] Based on the above embodiments, the outer ring and inner ring of the idler roller bearing 14 are axially positioned by the spiral sealing cap 23 and the spiral sealing stationary ring 22, respectively, and the spiral sealing cap 23 and the spiral sealing stationary ring 22 are axially positioned by the idler roller bearing 14.

[0076] In this embodiment, as Figure 2-6 As shown, the spiral sealing ring 21 is bolted to the gland side plate 23-2 to achieve synchronous movement of the spiral sealing ring 21, the spiral sealing gland 23, and the idler roller cylinder 12. A spiral sealing ring positioning part 21-3 is provided on one side of the spiral sealing ring 21. The side wall of the spiral sealing ring positioning part 21-3 abuts against the inner wall of the gland side plate 23-2, and a third static sealing ring 21-4 is provided between the spiral sealing ring positioning part 21-3 and the inner wall of the gland side plate 23-2. The third static sealing ring 21-4 provides a static seal between the spiral sealing gland 23 and the spiral sealing ring 21. Several spiral grooves 21-5 with equal cross-sections are evenly opened on the inner wall of the spiral sealing ring 21. Specifically, in this embodiment, spiral sealing rings 21 are provided on both the left and right sides of the idler roller assembly 1. When the idler roller cylinder 12 rotates, as... Figure 1 and Figure 3-6 As shown, Figure 6The middle arrow indicates that when viewed from the left side of the idler roller, the spiral sealing ring 21 rotates counterclockwise. In this case, when viewed from the right side of the idler roller, the spiral sealing ring 21 rotates clockwise. Since the spiral sealing ring 21 rotates with the idler roller body 12 via the spiral sealing cap 23 and bearing seat 13, when viewed from the right side of the idler roller, the rotation direction of the idler roller body 12 is clockwise. Taking the water self-sealing assembly 1 on the right side of the idler roller as an example... Figure 5 and Figure 6 The spiral sealing ring 21 on the right side of the idler assembly 1 shown has several equal-section spiral grooves 21-5, all of which are left-handed spiral grooves. These left-handed equal-section spiral grooves 21-5 on the right side of the idler assembly 1 reduce pressure on their corresponding variable-section spiral grooves 21-2 through a pumping effect. Furthermore, on the spiral sealing ring 21 on the right side of the idler assembly 1, the rotation direction of the variable-section spiral groove 21-2 to the left of the pressure-reducing groove 21-1 is the same as the rotation direction of its corresponding equal-section spiral groove 21-5. Figure 5As shown, the several variable cross-section spiral grooves 21-2 on the left side of the pressure-gathering groove 21-1 on the spiral sealing ring 21 are all left-hand spiral grooves, while the variable cross-section spiral grooves 21-2 on the right side of the pressure-gathering groove 21-1 on the spiral sealing ring 21 are right-hand spiral grooves; at the same time, the water self-sealing component 2 on the left side of the idler roller assembly 1 and the water self-sealing component 2 on the right side of the idler roller assembly 1 are symmetrically arranged, and the spiral grooves 21-5 of the equal cross-section of the water self-sealing component 2 on the left side of the idler roller assembly 1 and the water self-sealing component 2 on the right side of the idler roller assembly 1 have opposite directions of rotation; that is, when viewed from the right side of the idler roller, the water self-sealing component 2 on the left side of the idler roller assembly 1 has opposite directions of rotation to the water self-sealing component 2 on the right side of the idler roller assembly 1. When the roller body 12 rotates clockwise, the several equal-section spiral grooves 21-5 on the left spiral sealing ring 21 of the idler roller assembly 1 are all right-hand spiral grooves. On the spiral sealing ring 21, the variable-section spiral groove 21-2 to the right of the pressure-gathering groove 21-1 is a right-hand spiral groove, and the variable-section spiral groove 21-2 to the left of the pressure-gathering groove 21-1 is a left-hand spiral groove. It should be noted that when the rotation direction of the idler roller body 12 is viewed from the right side of the idler roller and is counterclockwise, the equal-section spiral grooves 21-5 in the water self-sealing assembly 2 are... Furthermore, the rotation direction of the variable cross-section spiral groove 21-2 is opposite to that of the constant cross-section spiral groove 21-5 and the variable cross-section spiral groove 21-2 when the roller cylinder 12 is rotated clockwise as observed from the right side of the roller. That is, several constant cross-section spiral grooves 21-5 on the right spiral sealing ring 21 of the roller assembly 1 are all right-hand spiral grooves. On this spiral sealing ring 21, the rotation direction of the variable cross-section spiral groove 21-2 on the left side of the pressure-gathering groove 21-1 is all right-hand, and the rotation direction of the variable cross-section spiral groove 21-2 on the right side of the pressure-gathering groove 21-1 is all right-hand. The spiral is left-handed; at this time, the several equal-section spiral grooves 21-5 on the left spiral sealing ring 21 of the idler roller assembly 1 are all left-handed spiral grooves. On the spiral sealing ring 21, the variable cross-section spiral groove 21-2 on the right side of the pressure-gathering groove 21-1 is a left-handed spiral groove, and the variable cross-section spiral groove 21-2 on the left side of the pressure-gathering groove 21-1 is a right-handed spiral groove. There are gaps between the spiral sealing ring 21 and the idler roller shaft 11, between the spiral sealing ring 21 and the spiral sealing stationary ring 22, and between the spiral sealing stationary ring 22 and the spiral sealing pressure ring 24.

[0077] Based on the above embodiments, the present invention provides a water self-sealing component on the outside of the idler bearing 14 in the idler assembly 1. The spiral sealing moving ring 21, the spiral sealing stationary ring 22, and the spiral sealing gland 23 together form a unique leakage path, specifically as follows: Figure 24 As described above, the direction indicated by the arrow in the figure is the leakage path; the variable cross-section spiral groove 21-2 on the outer circumference of the spiral sealing ring 21 generates a fluid pumping effect facing the shaft center during rotation, causing the sealed medium to accumulate inside the pressure-gathering groove 21-1, and forming a large sealing pressure inside the pressure-gathering groove 21-1 to seal the roller bearing 14; the water between the roller shaft 11 and the spiral sealing ring 21 can reduce the pressure of the sealed medium under the action of the constant cross-section spiral groove 21-5, reducing the pressure of the sealed medium when it reaches the variable cross-section spiral groove 21-2, and further improving the sealing effect.

[0078] In this embodiment, as Figure 16-23 As shown, two first centrifugal sealing assemblies 3 are respectively disposed on one side of two water self-sealing assemblies 2, and the two first centrifugal sealing assemblies 3 are symmetrically disposed at the left and right ends of the idler roller assembly 1. Each first centrifugal sealing assembly 3 includes a centrifugal sealing moving ring 31 and a centrifugal sealing stationary ring 32. One side of the centrifugal sealing moving ring 31 is connected to the inner wall of the bearing seat 13, and the centrifugal sealing stationary ring 32 is sleeved on the idler roller shaft 11. One side of the centrifugal sealing stationary ring 32 and one side of the centrifugal sealing moving ring 31 together form a static sealing cavity 33. A hollow centrifugal sleeve 34 is provided inside the static sealing cavity 33. A T-shaped sealing ring 35 and a first preload spring 37 are provided inside the centrifugal sleeve 34. The T-shaped sealing ring 35 includes a sealing part 35-1 and an abutment part 35-2. The inner diameter side of the abutment part 35-2 is provided to connect with the inner wall of the centrifugal sleeve 34. The first pre-tension spring 37 has several centrifugal rotation mechanisms 36 symmetrically arranged on both sides of the abutment portion 35-2; the sealing portion 35-1 extends out of the centrifugal sleeve 34 under the pressure of the first pre-tension spring 37 and abuts against the inner wall of the centrifugal sealing ring 32, forming a seal when the idler is static, preventing dust and water from the external environment from entering the interior of the idler assembly 1, ensuring that the idler plays a sealing role under static conditions; when the idler rotates, the centrifugal rotation mechanism 36 presses the sealing portion 35-1 of the T-shaped sealing ring 35 into the interior of the centrifugal sleeve 34 under the action of centrifugal force, so that the sealing portion 35-1 and the inner wall of the centrifugal sealing ring 32 form a gap, allowing dust or water from the external environment to reach the spiral groove sealing gap c of the water self-sealing assembly 2 through the second centrifugal sealing gap 43, wherein the spiral groove sealing gap c is as follows Figure 4 As shown.

[0079] Among them, such as Figure 16-18As shown, the centrifugal sealing ring 31 has a U-shaped cross-section. The centrifugal sealing ring 31 includes an integrally formed centrifugal sealing ring outer sleeve 31-1, a connecting part 31-2, and a centrifugal sealing ring inner sleeve 31-3. A fourth static sealing ring 13-2 is provided between the centrifugal sealing ring outer sleeve 31-1 and the bearing seat 13. The fourth static sealing ring 13-2 is embedded in the outer wall of the centrifugal sealing ring outer sleeve 31-1, achieving a static seal between the centrifugal sealing ring 31 and the bearing seat 13 to prevent leakage. One end of the centrifugal sealing ring outer sleeve 31-1 is connected to the spiral sealing cap 23. The side walls abut against each other. The outer sleeve 31-1 of the centrifugal rotating ring and the inner sleeve 31-3 of the centrifugal rotating ring are connected by the connecting part 31-2. One side of the connecting part 31-2 is provided with a third positioning groove 13-3 for installing the elastic retaining ring. The third positioning groove 13-3 is opened on the inner wall of the bearing seat 13. The two sides of the centrifugal sealing rotating ring 31 are axially positioned by the side wall of the spiral sealing cover 23 and the elastic retaining ring in the third positioning groove 13-3. The inner sleeve 31-3 of the centrifugal rotating ring is sleeved on the outside of the idler roller shaft 11, and a gap is provided between the inner sleeve 31-3 of the centrifugal rotating ring and the idler roller shaft 11.

[0080] Specifically, such as Figure 16 and Figure 17 As shown, the centrifugal sealing stationary ring 32 has an L-shaped cross-section. The centrifugal sealing stationary ring 32 includes an integrally formed centrifugal stationary ring sleeve 32-1 and a centrifugal stationary ring side plate 32-2. The centrifugal stationary ring sleeve 32-1 is located between the centrifugal moving ring outer sleeve 31-1 and the centrifugal moving ring inner sleeve 31-3. The centrifugal stationary ring side plate 32-2 is sleeved on the idler roller shaft 11. A centrifugal stationary ring positioning part 32-3 is provided at the inner diameter of the centrifugal stationary ring side plate 32-2. A fifth static sealing ring 32-4 is provided between the inner diameter side of the centrifugal static ring 32 and the idler roller shaft 11. One side of the centrifugal static ring positioning part 32-3 abuts against the shoulder of the idler roller shaft 11. The other side of the centrifugal static ring positioning part 32-3 is provided with a fourth positioning groove 11-3 for installing an elastic retaining ring. The fourth positioning groove 11-3 is opened on the idler roller shaft 11. The two sides of the centrifugal sealing static ring 32 are axially positioned by the shoulder of the idler roller shaft 11 and the elastic retaining ring in the fourth positioning groove 11-3.

[0081] In this embodiment, as Figure 16-17 and Figure 19-21As shown, the centrifugal sleeve 34 is disposed between the outer sleeve 31-1 and the inner sleeve 31-3 of the centrifugal rotating ring. The centrifugal sleeve 34 includes an outer ring 34-2, an inner ring 34-3, and a mounting ring 34-4. The mounting ring 34-4 is sleeved on the inner sleeve 31-1 of the centrifugal rotating ring. The outer ring 34-2 and the inner ring 34-3 are respectively disposed on both sides of the mounting ring 34-4. The outer ring 34-2 abuts against the side wall of the connecting part 31-2. One side of the inner ring 34-3 is provided with a fifth positioning groove 34-1 for installing an elastic retaining ring. The fifth positioning groove 34-1 is opened on the side wall of the inner sleeve 31-3 of the centrifugal rotating ring. The elastic retaining ring in the groove 34-1 provides axial positioning for the centrifugal sleeve 34; a sliding port is provided between the inner ring 34-3 and the outer ring 34-2, and the sealing part 35-1 of the T-shaped sealing ring 35 extends to the outside of the centrifugal sleeve 34 through the sliding port and abuts against the inner wall of the centrifugal stationary ring sleeve 32-1; the T-shaped sealing ring 35 is composed of several sealing ring segments connected end to end, and each sealing ring segment has a locking part 35-3 at both ends, and the locking parts 35-3 at both ends of each sealing ring segment are staggered, with a gap between adjacent sealing ring segments, to ensure that the T-shaped sealing ring 35 can be pressed into the interior of the centrifugal sleeve 34.

[0082] Specifically, several centrifugal rotating mechanisms 36 are evenly arranged on both sides of the T-shaped sealing ring 35. Each centrifugal rotating mechanism 36 includes a mounting base 36-1 installed inside the centrifugal sleeve 34. A centrifugal block 36-2 is rotatably connected to the mounting base 36-1 via a pin. The centrifugal block 36-2 has a centrifugal part 36-3 and a contact part 36-4 at both ends. The weight of the centrifugal part 36-3 is greater than the weight of the contact part 36-4. The contact part 36-4 cooperates with the groove on the abutment part 35-2. When the centrifugal rotating mechanism 36 rotates, the centrifugal part 36-3 gradually moves away from the mounting base 36-1 under the action of centrifugal force, causing the centrifugal block 36-2 to rotate around the pin that is rotatably connected to the mounting base 36-1. At this time, the contact part 36-4 at one end of the centrifugal block 36-2 presses down, pressing the T-shaped sealing ring 35 into the interior of the centrifugal sleeve 34, so that the sealing part 35-1 and the inner wall of the centrifugal sealing ring 32 form a gap.

[0083] Based on the above embodiments, when the idler roller cylinder 12 rotates, the T-shaped sealing ring 35 in the first centrifugal sealing assembly 3 disengages from the inner wall of the centrifugal static sealing ring 32 under the action of centrifugal force; when the idler roller cylinder 12 is stationary, the T-shaped sealing ring 35 abuts against the inner wall of the centrifugal static sealing ring 32 under the action of the first pre-tightening spring 37, thereby achieving a static seal on the idler roller assembly 1 and preventing external liquid from entering the interior of the idler roller assembly 1; each idler roller bearing 14 is provided with a water self-sealing assembly 2 and a first centrifugal sealing assembly 3 on its outer side, and a dynamic seal on the idler roller assembly 1 is achieved through the water self-sealing assembly 2, the first centrifugal sealing assembly 3, and the second centrifugal sealing assembly 4. Specifically, when the idler roller assembly 1 rotates, the first centrifugal sealing assembly 3 and the second centrifugal sealing assembly 4 rotate and open under the action of centrifugal force, that is, the centrifugal rotation mechanism in the first centrifugal sealing assembly 3 completely presses the T-shaped sealing ring 35 into the interior of the centrifugal sleeve 34 under the action of centrifugal force, and the sealing retaining ring 42 in the second centrifugal sealing assembly 4 completely presses into the T-shaped sealing ring 35 under the action of centrifugal force. Inside cavity 24-2, the roller shaft cylinder 12 can rotate smoothly. At this time, the external sealed medium can reach the water self-sealing component 2 and prevent the external sealed medium from entering the interior of roller assembly 1. At the same time, the first centrifugal sealing component 3 and the second centrifugal sealing component 4 achieve static sealing of roller assembly 1. Specifically, when roller assembly 1 is stationary, the abutting part 35-1 of the T-shaped sealing ring 35 in the first centrifugal sealing component 3 abuts against the inner wall of the centrifugal stationary ring sleeve 32-1 through the pre-tightening force of the first pre-tightening spring 37, and the sealing retaining ring 42 in the second centrifugal sealing component 4 abuts against the outer wall of the spiral sealing stationary ring 22 through the pre-tightening force of the second pre-tightening spring 41. The water self-sealing component 2, the first centrifugal sealing component 3 and the second centrifugal sealing component 4 on both sides of roller assembly 1 are sealed to prevent external water and dust from entering the interior of roller assembly 1, and at the same time prevent external water and dust from affecting the normal operation of roller bearing 14.

[0084] The sealed medium outside the idler roller is external water or dust, such as... Figure 23 and Figure 24 As shown, Figure 23 The direction indicated by the middle arrow is the path of the water flow. Figure 24 The direction indicated by the middle arrow is the diffusion and flow path of the external dust. In this embodiment, as... Figure 14-15As shown in Figures 22-24, when the roller cylinder 12 rotates, the sealing retaining ring 42 in the second centrifugal sealing assembly 4 compresses the second pre-tightening spring 41 under the action of centrifugal force, separates from the spiral sealing stationary ring 22, and forms the second centrifugal sealing gap 43. At the same time, the T-shaped sealing ring 35 in the first centrifugal sealing assembly 3 forms the first centrifugal sealing gap 38 between itself and the inner wall of the centrifugal stationary sealing ring 32 under the action of centrifugal force. The interior of the roller assembly 1 is connected to the outside through the second centrifugal sealing gap 43, the spiral groove sealing gap c, and the first centrifugal sealing gap 38.

[0085] During the rotation of the idler roller cylinder 12, if the sealed medium is water, since the idler roller cylinder 12 is rotating, the idler roller cylinder 12 drives the spiral sealing ring 21 to rotate through the spiral sealing cap 23. As the spiral sealing ring 21 rotates, external water will pass through it... Figure 23 The path reaches the spiral groove sealing gap c, where the variable cross-section spiral groove 21-2, through a pumping effect, gathers the sealing medium inside the pressure-gathering groove 21-1 to form sealing pressure, preventing external water from entering the interior of the idler assembly 1, thereby protecting the idler bearing 14; if the sealed medium is dust, the external dust will pass through... Figure 24 The path reaches the second centrifugal sealing gap 43. At this time, the dust is sealed by the grease added in the annular groove 22-3, preventing external dust from entering the interior of the idler roller assembly 1.

[0086] It should be noted that before the water medium being sealed reaches the variable cross-section spiral groove 21-2 in the water self-sealing assembly 2 to seal the water, the water being sealed needs to pass through the throttling and pressure reduction effect of the first centrifugal sealing gap 38 and the pumping and pressure reduction effect of the equal cross-section spiral groove 21-5 opened on the inner wall of the spiral sealing ring 21 in sequence, to further improve the sealing effect; before the dust medium being sealed reaches the grease in the annular groove 22-3 in the water self-sealing assembly 2 to seal the dust, the dust being sealed needs to pass through the throttling and pressure reduction effect of the first centrifugal sealing gap 38, the pumping and pressure reduction effect of the equal cross-section spiral groove 21-5 opened on the inner wall of the spiral sealing ring 21 in sequence, and the throttling and pressure reduction effect of the spiral groove sealing gap c in sequence, to further improve the sealing effect.

[0087] Furthermore, when the idler roller cylinder 12 is stationary, a portion of the sealed medium from outside the idler roller assembly 1 remains in the water self-sealing assembly 2. The second centrifugal sealing assembly 4 performs a static seal on the sealed medium remaining in the water self-sealing assembly 2, while the first centrifugal sealing assembly 3 seals the external sealed medium. Figure 22 As shown, in Figure 22 The direction indicated by the arrow in the first centrifugal sealing assembly 3 is the flow path of the external water.

[0088] like Figure 25 and Figure 26 As shown, this application also provides a mining belt conveyor equipped with idlers with the aforementioned water self-sealing and centrifugal sealing devices. The mining belt conveyor also includes a belt conveyor body 5 and several idler modules.

[0089] Among them, such as Figure 25 As shown, the belt conveyor body 5 includes a drive roller 51 and a driven roller 52. The drive roller 51 is connected to a power assembly, which provides rotational power to the drive roller 51. The drive roller 51 and the driven roller 52 are connected to the conveyor belt 53 and rotate together. The drive roller 51 and the driven roller 52 are respectively located at both ends of the conveyor belt 53.

[0090] It should be noted that this application only addresses the sealing problem in the idler rollers and applies it to mining belt conveyors. Therefore, the power components that drive the belt conveyor are not limited here, and the commonly used drive methods for belt conveyors in the prior art can be used.

[0091] like Figure 26 As shown, several idler modules are evenly distributed on the belt conveyor body 5 via support frames, and all idler modules are located between the drive drum 51 and the driven drum 52. Each idler module includes three sets of idler assemblies 1 above the support frame and one set of idler assemblies 1 below the support frame. Above the support frame, the three sets of idler assemblies 1 form a U-shaped idler trough, which supports the conveyor belt 53. The idler assemblies 1 below the support frame work together with the idler assemblies 1 above the support frame to move the conveyor belt 53. It should be noted that... Figure 26 Although there are two labels 1, these two labels 1 represent the same idler roller assembly 1, with only differences in installation position and size.

[0092] The present invention provides a mining belt conveyor, which adopts idlers equipped with water self-sealing and centrifugal sealing devices. Under various complex working conditions such as high dust, high humidity and water immersion in coal mines, the idlers can maintain the normal working state of dynamic and static seals, thereby ensuring the long-term safe and stable operation of the belt conveyor.

[0093] Finally, it should be noted that the above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art can still modify the technical solutions described in the foregoing embodiments or make equivalent substitutions for some of the technical features. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. A roller of a water-sealed and centrifugal sealing device, characterized in that, It includes an idler roller assembly, and both the left and right sides of the idler roller assembly are equipped with a water self-sealing assembly and a first centrifugal sealing assembly. The idler assembly includes an idler shaft, an idler cylinder is sleeved on the outside of the idler shaft, bearing seats are provided at both ends of the inner side of the idler cylinder, an idler bearing is provided between each bearing seat and the idler shaft, and a water self-sealing component and a first centrifugal sealing component are provided on the outside of each idler bearing. Two water-sealing assemblies are respectively located on one side of the two idler roller bearings, and the two water-sealing assemblies are symmetrically arranged on the left and right sides of the idler roller assembly. Each water-sealing assembly includes a spiral sealing moving ring and a spiral sealing stationary ring. The spiral sealing moving ring is connected to the bearing housing through a spiral sealing cap. A pressure-gathering groove is opened in the middle of the outer diameter of the spiral sealing moving ring, and several variable cross-section spiral grooves are symmetrically opened on both sides of the pressure-gathering groove. The width and depth of the variable cross-section spiral grooves gradually decrease from the outside to the inside. The spiral sealing stationary ring is sleeved on the idler roller shaft, and one end of the spiral sealing stationary ring extends between the spiral sealing moving ring and the spiral sealing cap. The spiral sealing moving ring and the spiral sealing stationary ring together form a spiral dynamic seal to water-seale the idler roller bearing. Two first centrifugal sealing assemblies are respectively located on one side of two water self-sealing assemblies, and the two first centrifugal sealing assemblies are symmetrically located at the left and right ends of the idler roller assembly. Each first centrifugal sealing assembly includes a centrifugal sealing moving ring and a centrifugal sealing stationary ring. One side of the centrifugal sealing moving ring is connected to the inner wall of the bearing seat, and the centrifugal sealing stationary ring is sleeved on the idler roller shaft. One side of the centrifugal sealing stationary ring and one side of the centrifugal sealing moving ring together form a static sealing cavity. A hollow centrifugal sleeve is provided inside the static sealing cavity. A T-shaped sealing ring is provided inside the centrifugal sleeve. The T-shaped sealing ring includes a sealing part and an abutting part. The sealing part extends to the outside of the centrifugal sleeve and abuts against the inner wall of the centrifugal sealing stationary ring. A first pre-tightening spring is provided on the inner diameter side of the abutting part and is connected to the inner wall of the centrifugal sleeve. Several centrifugal rotating mechanisms are symmetrically arranged on both sides of the abutting part. Under the action of centrifugal force, the sealing part of the T-shaped sealing ring is pressed into the interior of the centrifugal sleeve by the centrifugal rotating mechanisms.

2. The idler roller of the water self-sealing and centrifugal sealing device according to claim 1, characterized in that, The spiral sealing cap has an L-shaped cross-section and includes an integrally formed cap side plate and a cap sleeve with a stepped inner wall. A first static sealing ring is provided between the outer wall of the cap side plate and the centrifugal sealing moving ring, and the first sealing ring is embedded in the side wall of the cap side plate. A spiral sealing ring is provided at the stepped inner wall of the cap sleeve. One end of the spiral sealing ring has a positioning protrusion, which is located between the outer ring of the idler roller bearing and the cap sleeve. The other end of the spiral sealing ring and the stepped side wall of the cap sleeve together form a T-shaped cavity. A second centrifugal sealing assembly is installed in the T-shaped cavity. The second centrifugal sealing assembly includes a second pre-tightening spring connected to the inner wall of the cap sleeve. One end of the second pre-tightening spring is connected to a sealing retaining ring. One end of the sealing retaining ring abuts against the outer wall of the spiral sealing static ring, and the axial sides of the sealing retaining ring are limited by the cap sleeve and the spiral sealing ring, respectively.

3. The idler roller of the water self-sealing and centrifugal sealing device according to claim 2, characterized in that, The spiral sealing stationary ring has an L-shaped cross-section and includes an integrally formed spiral stationary ring sleeve and a spiral stationary ring side plate. The spiral stationary ring sleeve is located between the spiral sealing pressure ring and the spiral sealing moving ring. Several annular grooves are formed on the outer wall of the spiral stationary ring sleeve. The spiral stationary ring side plate is sleeved on the idler roller shaft. The inner diameter of the spiral stationary ring side plate is provided with a spiral stationary ring positioning part that abuts against the inner ring of the idler roller bearing. One side of the idler roller bearing is provided with a first positioning groove for installing a bearing retaining ring, and a bearing washer is provided between this side of the idler roller bearing and the corresponding bearing seat side wall. One side of the spiral stationary ring positioning part is provided with a second positioning groove for installing an elastic retaining ring. Both the first and second positioning grooves are formed on the idler roller shaft. A second stationary sealing ring is provided between the spiral stationary ring positioning part and the idler roller shaft.

4. The idler roller of the water self-sealing and centrifugal sealing device according to claim 3, characterized in that, The spiral sealing ring is bolted to the side plate of the gland. A spiral sealing ring positioning part is provided on one side of the spiral sealing ring. The side wall of the spiral sealing ring positioning part abuts against the inner wall of the gland side plate, and a third static sealing ring is provided between the spiral sealing ring positioning part and the inner wall of the gland side plate. Several equal-section spiral grooves are evenly distributed on the inner wall of the spiral sealing ring. When the rotation direction of the idler roller cylinder is clockwise when viewed from the right side of the idler roller, several equal-section spiral grooves on the spiral sealing ring on the right side of the idler roller assembly are left-hand spiral grooves. On the spiral sealing ring on the right side of the idler roller assembly, the rotation direction of the variable-section spiral groove to the left of the pressure-gathering groove is the same as the rotation direction of its corresponding equal-section spiral groove. Several equal-section spiral grooves on the spiral sealing ring on the left side of the idler roller assembly are right-hand spiral grooves. On the sealing ring, the spiral groove with variable cross-section on the right side of the pressure-gathering groove has the same rotation direction as its corresponding constant cross-section spiral groove. When the rotation direction of the idler roller body is counterclockwise when viewed from the right side of the idler roller, several constant cross-section spiral grooves on the right spiral sealing ring of the idler roller assembly are all right-hand spiral grooves. On this spiral sealing ring, the spiral groove with variable cross-section on the left side of the pressure-gathering groove has the same rotation direction as its corresponding constant cross-section spiral groove. Several constant cross-section spiral grooves on the left spiral sealing ring of the idler roller assembly are all left-hand spiral grooves. On the spiral sealing ring on the left side of the idler roller assembly, the spiral groove with variable cross-section on the right side of the pressure-gathering groove has the same rotation direction as its corresponding constant cross-section spiral groove. Gaps are provided between the spiral sealing ring and the idler roller shaft, between the spiral sealing ring and the spiral sealing stationary ring, and between the spiral sealing stationary ring and the spiral sealing pressure ring.

5. The idler roller of the water self-sealing and centrifugal sealing device according to claim 4, characterized in that, The ratio between the outer groove width and the inner groove width of the variable cross-section spiral groove ranges from 1 to 3, the ratio between the outer groove depth and the inner groove depth ranges from 1 to 3, and the helix angle of the variable cross-section spiral groove is 10 to 30°. When the inner groove width and inner groove depth of the variable cross-section spiral groove are constant, the formula for the total sealing pressure P under different outer groove widths A, different outer groove depths B, and different helix angles β is: P﹦148.1﹣17.45×A﹢17.84×B﹣58.95×β﹣89.35×AB﹣43.3×Aβ﹣37.05×Bβ﹢60.87×A 2 ﹢61.22×B 2 ﹢78.85×β 2 ; The unit of the total sealing pressure P is kPa.

6. The idler roller of the water self-sealing and centrifugal sealing device according to claim 1, characterized in that, The centrifugal sealing ring has a U-shaped cross-section and includes an integrally formed centrifugal sealing ring outer sleeve, a connecting part, and a centrifugal sealing ring inner sleeve. A fourth static sealing ring is provided between the centrifugal sealing ring outer sleeve and the bearing seat, and the fourth static sealing ring is embedded in the outer wall of the centrifugal sealing ring outer sleeve. One end of the centrifugal sealing ring outer sleeve abuts against the side wall of the spiral sealing cover. The centrifugal sealing ring outer sleeve and the centrifugal sealing ring inner sleeve are connected by the connecting part. A third positioning groove for installing an elastic retaining ring is provided on one side of the connecting part. The third positioning groove is opened on the inner wall of the bearing seat. The centrifugal sealing ring inner sleeve is sleeved on the outside of the idler roller shaft, and a gap is provided between the centrifugal sealing ring inner sleeve and the idler roller shaft.

7. The idler roller of the water self-sealing and centrifugal sealing device according to claim 6, characterized in that, The centrifugal sealing stationary ring has an L-shaped cross-section and includes an integrally formed centrifugal stationary ring sleeve and a centrifugal stationary ring side plate. The centrifugal stationary ring sleeve is located between the outer sleeve of the centrifugal moving ring and the inner sleeve of the centrifugal moving ring. The centrifugal stationary ring side plate is sleeved on the idler roller shaft. A centrifugal stationary ring positioning part is provided at the inner diameter of the centrifugal stationary ring side plate. A fifth stationary sealing ring is provided between the inner diameter side of the centrifugal stationary ring positioning part and the idler roller shaft. One side of the centrifugal stationary ring positioning part abuts against the shoulder of the idler roller shaft. A fourth positioning groove for installing an elastic retaining ring is provided on the other side of the centrifugal stationary ring positioning part. The fourth positioning groove is opened on the idler roller shaft.

8. The idler roller of the water self-sealing and centrifugal sealing device according to claim 7, characterized in that, The centrifugal sleeve is disposed between the outer sleeve and the inner sleeve of the centrifugal rotating ring. The centrifugal sleeve includes an outer ring, an inner ring, and a mounting ring. The mounting ring is sleeved on the inner sleeve of the centrifugal rotating ring. The outer ring and the inner ring are respectively disposed on both sides of the mounting ring. The outer ring abuts against the side wall of the connecting part. One side of the inner ring is provided with a fifth positioning groove for installing the elastic retaining ring. The fifth positioning groove is opened on the side wall of the inner sleeve of the centrifugal rotating ring. A sliding opening is provided between the inner ring and the outer ring. The sealing part of the T-shaped sealing ring extends to the outside of the centrifugal sleeve through the sliding opening and abuts against the inner wall of the centrifugal stationary ring sleeve. The T-shaped sealing ring is composed of several sealing ring segments connected end to end. Each sealing ring segment has a locking part at both ends, and the locking parts at both ends of each sealing ring segment are staggered. There is a gap between two adjacent sealing ring segments.

9. The idler roller of the water self-sealing and centrifugal sealing device according to claim 8, characterized in that, Several centrifugal rotating mechanisms are evenly arranged on both sides of the T-shaped sealing ring. Each centrifugal rotating mechanism includes a mounting base installed inside the centrifugal sleeve. A centrifugal block is rotatably connected to the mounting base via a pin. The centrifugal block has a centrifugal part and a contact part at both ends. The weight of the centrifugal part is greater than the weight of the contact part. The contact part and the groove on the abutment part cooperate.

10. A mining belt conveyor, characterized in that, The mining belt conveyor further includes idlers with water self-sealing and centrifugal sealing devices as described in any one of claims 1-9, and also includes: The belt conveyor body includes a drive roller and a driven roller. The drive roller is connected to a power component, which provides rotational power to the drive roller. The drive roller and the driven roller are connected to a conveyor belt and rotate together. The drive roller and the driven roller are respectively located at both ends of the conveyor belt. Several idler modules are evenly distributed on the belt conveyor body via support frames, and the idler modules are located between the drive drum and the driven drum. Each idler module includes three sets of idler assemblies located above the support frame and one set of idler assemblies located below the support frame. Above the support frame, the three sets of idler assemblies form a U-shaped idler trough, which is used to support the conveyor belt. The idler assemblies below the support frame work together with the idler assemblies above the support frame to move the conveyor belt.

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