A sealing structure of a sintering trolley wheel and a sintering trolley wheel assembly

Abstract

The application relates to a sealing structure of a sintering trolley wheel, which comprises an axle and a wheel; the wheel is rotatably arranged on the axle through a bearing; a sealing piece is arranged between the wheel and the axle, the sealing piece is provided with two groups, and the two groups of sealing pieces are respectively arranged on the two axial sides of the bearing; wherein the sealing piece comprises a plurality of sealing sheets arranged in sequence along the axle, in the two adjacent sealing sheets, one is mounted on the axle, and the other is mounted on the wheel, so that the plurality of sealing sheets form a labyrinth sealing channel in the space between the axle and the wheel; the labyrinth sealing channel is filled with sealing grease. Meanwhile, a sintering trolley wheel assembly is provided. The sealing structure of the sintering trolley wheel can better block the invasion of external dust and prevent grease loss, avoid dry grinding of the sealing sheet, improve the sealing reliability, and prolong the service life of the sealing piece, the wheel and the trolley.

Description

Technical Field

[0001] This invention relates to the field of sintering trolley technology, and in particular to a sealing structure for a sintering trolley wheel and a sintering trolley wheel assembly. Background Technology

[0002] like Figure 1 As shown, in the sintering trolley, a lip seal 3 is usually used to seal between the wheel 1 and the axle 2 to prevent external dust and other impurities from entering the bearing cavity and to prevent internal lubricating grease from leaking. However, the sintering trolley operates in a high-temperature and high-dust environment for a long time, and experiences significant alternating high and low temperature changes within an operating cycle, making the working conditions of the lip seal 3 extremely harsh.

[0003] Due to the repeated temperature changes during the operation of the sintering trolley, the lubricating grease inside the sealing cavity will expand and contract accordingly, resulting in a periodic pressure difference between the inside and outside of the sealing cavity. This causes the lip seal 3 to exhibit a "breathing effect." When the temperature inside the sealing cavity drops, the grease contracts, and external dust is easily drawn into the sealing cavity through the lip or mating gap; when the temperature rises, the grease is squeezed outward. This repeated breathing action causes external dust to continuously enter and accumulate in the lip and sealing cavity, disrupting the cleanliness of the sealing interface.

[0004] Meanwhile, the high-temperature environment reduces the viscosity of the sealing grease, accelerates its volatilization and oxidation, and factors such as internal and external pressure fluctuations caused by the breathing effect and vibrations during trolley operation further promote the loss of sealing grease from the lip. As the sealing grease gradually flows out, it becomes difficult to form a continuous and effective lubricating oil film between the lip of the lip seal 3 and the mating surface of the axle 2 or wheel 1. Dust particles entering the sealing cavity then participate in friction as abrasive particles, leading to dry friction and abrasive wear at the lip, resulting in problems such as aging, cracking, or excessive wear of the lip material, causing a rapid decline in sealing performance.

[0005] When the seal fails, external dust can more easily enter the bearing cavity, internal lubricating grease can be further lost, bearing lubrication conditions deteriorate, wheel rotation resistance increases, wheel and bearing wear is accelerated, the service life of the wheel is directly affected, and the overall service life of the sintering trolley is shortened, reducing the reliability and economy of equipment operation.

[0006] In addition, the chuck at the wheel structure also uses a lip seal, which also has the above-mentioned problems.

[0007] Currently, the sealing structure using lip seal 3 can only meet the sealing requirements of existing wheel structures. However, the service life of existing wheel structures is usually less than 3 years. When the wheel structure is improved and its service life is increased to more than 3 years, the existing sealing structure cannot meet the sealing requirements of this type of wheel structure, thus affecting the improvement of the service life of this type of long-life wheel structure.

[0008] Therefore, how to provide a new sealing structure for sintered trolley wheels to meet the sealing requirements of long-life wheel structures is a technical problem that urgently needs to be solved in this field. Summary of the Invention

[0009] This invention addresses the technical problem of existing sintering trolley lip seals, which are prone to dust inhalation and grease loss under high-temperature, high-dust, and temperature-alternating conditions, leading to dry friction and shortened wheel and trolley lifespan, and failing to meet the sealing requirements of long-life wheel structures. The invention provides a sealing structure for a sintering trolley wheel, comprising an axle and a wheel rotatably mounted on the axle via bearings. Seals are provided on both sides of the bearing axial direction between the wheel (and / or the chuck) and the axle. Each seal consists of multiple sealing plates arranged sequentially along the axle axial direction, with adjacent sealing plates alternately fixed to the axle and wheel. This forms a tortuous labyrinthine sealing channel within the annular space between the axle and wheel. The labyrinthine sealing channel is filled with grease to prevent external dust intrusion and grease loss, avoiding dry friction of the sealing plates, improving sealing reliability, and extending the service life of the seals, wheel, and trolley, thus better meeting the sealing requirements of long-life wheel structures.

[0010] A sealing structure for a sintered trolley wheel, comprising an axle, a wheel, and a retaining wheel; The wheel is rotatably mounted on the axle via bearings; The cam is rotatably mounted on the axle via a cam bearing; A seal is provided between the wheel and the axle. There are two sets of seals, and the two sets of seals are located on both sides of the axial direction of the bearing. The sealing element includes multiple sealing plates arranged sequentially along the axial direction of the axle. In two adjacent sealing plates, one is installed on the axle and the other is installed on the wheel, so that the multiple sealing plates form a labyrinth-like sealing channel in the space between the axle and the wheel. The labyrinthine sealed channel is filled with sealing grease. And / or, the cam seal includes multiple cam seal pieces arranged sequentially along the axial direction of the axle, wherein one of two adjacent cam seal pieces is installed on the axle and the other is installed on the cam, so that the multiple cam seal pieces form a labyrinthine cam seal channel in the space between the axle and the cam; The sealing channel of the caliper is filled with sealing grease.

[0011] Preferably, the sealing sheet installed on the axle is a first sealing sheet, and the sealing sheet installed on the wheel is a second sealing sheet; A first radial gap is left between the outer periphery of the first sealing sheet and the wheel; A second radial gap is left between the inner circumference of the second sealing sheet and the axle; The adjacent first and second sealing pieces overlap at least partially in the radial direction, and there is an axial gap between the overlapping portions. The axial gap communicates with the first radial gap and the second radial gap respectively, forming a tortuous labyrinthine sealing channel.

[0012] Preferably, the first radial gap and / or the second radial gap are eccentric annular gaps.

[0013] Preferably, the first sealing sheet and / or the second sealing sheet are eccentric annular sealing sheets, so that the first radial gap and / or the second radial gap form an eccentric annular gap.

[0014] Preferably, both the first sealing sheet and the second sealing sheet are eccentric annular sealing sheets, so that the first radial gap and the second radial gap form the eccentric annular gap.

[0015] Preferably, the cam seal installed on the axle is a first cam seal, and the cam seal installed on the cam is a second cam seal. A radial clearance is provided between the outer periphery of the first caliper sealing plate and the caliper; A radial clearance of the second cam seal is provided between the inner circumference of the second cam seal and the axle. The adjacent first and second chuck seals overlap at least partially in the radial direction, and there is an axial gap between the overlapping portions. The axial gap of the chuck communicates with the radial gaps of the first and second chucks respectively, forming a tortuous labyrinthine chuck sealing channel.

[0016] Preferably, the radial clearance of the first caliper and / or the radial clearance of the second caliper are eccentric annular clearances.

[0017] Preferably, both the first and second caliper seals are eccentric annular seals, so that the radial clearance of the first caliper and the radial clearance of the second caliper form an eccentric annular gap.

[0018] A sintering trolley wheel assembly, which utilizes the sealing structure of the sintering trolley wheel as described in any one of the above descriptions.

[0019] Compared with the prior art, the sealing structure of the sintering trolley wheel provided by the present invention includes multiple sealing plates arranged sequentially along the axial direction of the axle. Of two adjacent sealing plates, one is installed on the axle and the other on the wheel, forming a labyrinthine sealing channel within the space between the axle and the wheel. This labyrinthine sealing channel has a tortuous path, effectively preventing external dust from entering. Even under the influence of temperature fluctuations causing a breathing effect, dust is less likely to directly penetrate the bearing cavity, thus significantly reducing dust intake and improving sealing reliability. Furthermore, the labyrinthine sealing channel is filled with sealing grease. Constrained by the tortuous channel, the sealing grease is less likely to be lost under the vibration and breathing effect of the trolley operation, maintaining a long-term lubricated state and preventing dry friction and abrasive wear between the sealing plates and the axle or wheel, thereby extending the service life of the sealing element. Furthermore, the two sets of seals are located on both sides of the bearing axially, forming a symmetrical seal at both ends of the bearing. This further prevents dust and impurities from entering the bearing cavity from both sides, ensuring that the bearing is in a good lubrication state for a long time, thereby extending the overall service life of the wheel and sintering trolley and reducing equipment maintenance and downtime costs. Attached Figure Description

[0020] To more clearly illustrate the technical solutions in the embodiments of this application 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 this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0021] Figure 1 This is a schematic diagram of the cross-sectional structure of a sintering trolley wheel in the prior art; Figure 2 A three-dimensional structural schematic diagram of a sintering trolley wheel assembly provided in one embodiment; Figure 3 for Figure 2 A schematic cross-sectional view of the sintering trolley wheel assembly shown. Figure 4 for Figure 3 A magnified view of a portion of region B shown; Figure 5 A schematic diagram of the planar structure of the second sealing sheet and the adjusting member provided in one embodiment (the red area in the figure represents the second radial gap); Figure 6 A schematic diagram of the planar structure of a second sealing sheet provided in one embodiment; Figure 7 A schematic diagram of the planar structure of the first sealing sheet and the end cap provided in one embodiment (the red area in the figure represents the first radial gap). Figure 8 A schematic diagram of the planar structure of a first sealing sheet provided in one embodiment; Figure 9 for Figure 3 A magnified view of region C shown below; Figure 10 for Figure 3 A magnified view of region D shown below; Figure 11 for Figure 2 The diagram shows a planar structural schematic of the sintering trolley wheel assembly. Detailed Implementation

[0022] To enable those skilled in the art to better understand the technical solutions in this application, the technical solutions in the embodiments of this application will be clearly and completely described below. Obviously, the described embodiments are only a part of the embodiments of this application, and not all of the embodiments. Based on the embodiments in this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0023] It should be noted that when a component is referred to as being "mounted on", "fixed on", or "set on" another component, it can be directly on or indirectly set on the other component; when a component is referred to as being "connected to" another component, it can be directly connected to or indirectly connected to the other component.

[0024] It should be noted that the structures, proportions, sizes, etc., shown in the accompanying drawings are only for the purpose of assisting those skilled in the art in understanding and reading the content disclosed in the specification, and are not intended to limit the implementation conditions of this application. They should not be construed as limiting the scope of protection of this application. Any modifications to the structure, changes in the proportions, or adjustments to the size shall still fall within the scope of the technical content disclosed in this application, provided that they do not affect the effects and purposes that this application can produce.

[0025] This invention provides a sealing structure for a sintering trolley wheel, comprising an axle and a wheel; the wheel is rotatably mounted on the axle via a bearing; a seal is provided between the wheel and the axle, and two sets of seals are provided, each set located on one side of the axial direction of the bearing; wherein the seal comprises multiple sealing plates arranged sequentially along the axial direction of the axle, with one of two adjacent sealing plates mounted on the axle and the other on the wheel, so that the multiple sealing plates form a labyrinthine sealing channel in the space between the axle and the wheel; the labyrinthine sealing channel is filled with sealing grease. This sealing structure for the sintering trolley wheel can better prevent external dust intrusion and grease loss, avoid dry friction of the sealing plates, improve sealing reliability, and extend the service life of the seals, wheel, and trolley.

[0026] Please refer to the following: Figures 2 to 11 In one embodiment, a sealing structure for the wheel of a sintering trolley is provided, which is mainly used to solve the problem that the existing sintering trolley wheels use lip seals, and under long-term operation of the sintering trolley, the sealing grease at the lip seal is easily lost, resulting in dry friction of the lip seal and a decrease in sealing performance.

[0027] The sealing structure of the sintering trolley wheel includes an axle 10 and a wheel 20. The wheel 20 is rotatably mounted on the axle 10 via a bearing 30. Specifically, the bearing 30 is located radially inside the wheel 20. A seal 40 is provided between the wheel 20 and the axle 10. Two sets of seals 40 are provided, and the two sets of seals 40 are located on opposite axial sides of the bearing 30.

[0028] The sealing element 40 includes multiple sealing plates 41 arranged sequentially along the axial direction of the axle 10. Of two adjacent sealing plates 41, one is mounted on the axle 10 and the other on the wheel 20, so that the multiple sealing plates 41 form a labyrinthine sealing channel 50 within the space between the axle 10 and the wheel 20. The labyrinthine sealing channel 50 is filled with sealing grease.

[0029] In other words, the sealing element 40 adopts a stacked structure, and the multiple sealing plates 41 in the sealing element 40 are staggered on the axle 10 and the wheel 20. If one of two adjacent sealing plates 41 is installed on the axle 10, then the other is installed on the wheel 20. This results in one of the adjacent sealing plates 41 forming a radial sealing gap with the axle 10, and the other forming a radial sealing gap with the wheel 20. Furthermore, adjacent sealing plates 41 are staggered axially and radially, allowing these radial sealing gaps to connect sequentially through the axial gaps between adjacent sealing plates 41. This forms a labyrinthine sealing channel 50 that meanders axially and radially within the annular space between the axle 10 and the wheel 20. External dust must pass through multiple turns along the labyrinthine sealing channel 50 to enter the bearing cavity, significantly increasing flow resistance and effectively preventing external dust intrusion. It also better prevents the loss of internal sealing grease.

[0030] Understandably, existing technologies typically use polymer lip seals to seal between wheels and axles. However, sintering trolleys operate in high-temperature, high-dust environments for extended periods, experiencing significant alternating high and low temperature changes within a single operating cycle, making the working conditions for lip seals extremely harsh. During sintering trolley operation, repeated temperature fluctuations cause the grease inside the sealing cavity to expand and contract, resulting in a periodic pressure difference between the inside and outside of the sealing cavity, causing the lip seal to exhibit a "breathing effect." This repeated breathing allows external dust to continuously enter and accumulate at the lip and inside the sealing cavity, disrupting the cleanliness of the sealing interface. Simultaneously, the high-temperature environment reduces the viscosity of the sealing grease, accelerates its volatilization and oxidation, and the internal and external pressure fluctuations caused by the breathing effect, along with vibrations during trolley operation, further promote grease loss from the lip. As the sealing grease gradually leaks out, it becomes difficult to form a continuous and effective lubricating film between the lip of the lip seal and the mating surface of the axle or wheel. Dust particles entering the sealing cavity then participate in friction as abrasive particles, leading to dry friction and abrasive wear at the lip. This results in problems such as aging, cracking, or excessive wear of the lip material, causing a rapid decline in sealing performance. After the seal fails, external dust can more easily enter the bearing cavity, further causing internal lubricating grease to leak out. This deteriorates the bearing lubrication conditions, increases the wheel rotation resistance, accelerates the wear of the wheel and bearing, directly affects the wheel's service life, and consequently shortens the overall service life of the sintering trolley, reducing the reliability and economy of equipment operation.

[0031] In the sealing structure of the sintering trolley wheel provided in this embodiment, the sealing element 40 includes multiple sealing plates 41 arranged sequentially along the axial direction of the axle 10. Of two adjacent sealing plates 41, one is installed on the axle 10 and the other on the wheel 20, forming a labyrinthine sealing channel 50 within the space between the axle 10 and the wheel 20. This labyrinthine sealing channel 50 has a tortuous path, effectively increasing the flow resistance of external dust entering the bearing cavity. Even under the breathing effect caused by temperature fluctuations, dust is less likely to directly invade the bearing cavity, thus significantly reducing dust intake and improving sealing reliability. Furthermore, the labyrinthine sealing channel 50 is filled with sealing grease. Constrained by the tortuous channel, the sealing grease is less likely to be lost under the pressure fluctuations caused by the trolley's running vibration and breathing effect, maintaining a long-term lubricated state. This prevents dry friction and abrasive wear between the sealing plates 41 and the axle 10 or wheel 20 due to lack of oil, thereby extending the service life of the sealing element 40. Furthermore, the two sets of seals 40 are located on both sides of the axial direction of the bearing 30, forming a symmetrical seal at both ends of the bearing 30. This further prevents dust and impurities from entering the bearing cavity from both sides of the bearing 30, ensuring that the bearing 30 is in a good lubrication environment for a long time, thereby extending the overall service life of the wheel and sintering trolley and reducing equipment maintenance and downtime costs.

[0032] Preferably, in one embodiment, the sealing plate 41 installed on the axle 10 is a first sealing plate 4101, and the sealing plate 41 installed on the wheel 20 is a second sealing plate 4102. A first radial gap 51 is left between the outer periphery of the first sealing plate 4101 and the wheel 20, and a second radial gap 52 is left between the inner periphery of the second sealing plate 4102 and the axle 10. Adjacent first sealing plates 4101 and second sealing plates 4102 at least partially overlap radially, and an axial gap 53 is left between the overlapping portions. The axial gap 53 communicates with the first radial gap 51 and the second radial gap 52 respectively, forming a tortuous labyrinthine sealing channel 50. Wherein, adjacent first sealing plates 4101 and second sealing plates 4102 at least partially overlap radially means that the radial extension ranges of the two sealing plates 41 have overlapping areas. This design causes the first radial gap 51 and the second radial gap 52 to be staggered in the axial and radial directions, thus avoiding the formation of a straight leakage path. This forces external dust to flow back and forth radially and axially within the sealed channel, creating a labyrinthine sealing effect and increasing flow resistance. In this embodiment, through the above structural design, radial gaps are maintained between the first sealing plate 4101 and the wheel 20, and between the second sealing plate 4102 and the axle 10. Additionally, axial gaps are maintained between adjacent sealing plates 41, ensuring that the sealing plates 41 do not contact each other during normal operation. Structurally, this avoids dry friction and wear between the sealing plates 41 and between the sealing plates 41 and the axle 10 or the wheel 20. Simultaneously, the first radial gap 51, the second radial gap 52, and the axial gap 53 are interconnected to form a tortuous labyrinthine sealing channel 50. The path for external dust to enter the bearing cavity is significantly lengthened and complicated, increasing flow resistance. Even under the influence of a breathing effect caused by temperature fluctuations, external dust is less likely to directly intrude into the bearing cavity, effectively reducing dust intake. After the sealing grease is filled in the labyrinthine sealing channel 50, it is blocked and constrained by the tortuous channel and multiple sealing plates 41. Under the pressure fluctuations caused by the vibration of the trolley and the breathing effect, it is not easy to be lost. It can maintain a stable lubricating oil film in the sealing gap for a long time, further avoiding dry friction and improving the adsorption and blocking ability of dust, thereby extending the overall service life of the sealing element 40, the wheel and the sintering trolley.

[0033] Preferably, in one embodiment, the first radial gap 51 and / or the second radial gap 52 are eccentric annular gaps. An eccentric annular gap means that the width of the radial gap in the circumferential direction is not uniform, but rather unevenly distributed along the circumference. For example, when the center of the inner ring of the sealing plate 41 does not coincide with the center of the outer ring, or when the center of the corresponding part of the axle 10 or wheel 20 to which the sealing plate 41 engages does not coincide with the center of the sealing plate 41, the gap between the sealing plate 41 and the wheel 20 or axle 10 will be wider on one side and narrower on the other, forming an eccentric annular gap.

[0034] It is understandable that if the first radial gap 51 (the second radial gap 52) is set as a concentric annular gap, i.e., the gap is uniform along the circumference, the sealing grease will easily remain relatively stationary in the gap when the wheel 20 rotates, and will not be easily moved or renewed. However, the existing technology uses a lip seal, in which the sealing grease remains relatively stationary and is not easily moved or renewed. Furthermore, lip seals are prone to aging, cracking, and breakage under high-temperature conditions. During long-term operation of the sintering trolley and under high-temperature conditions, the sealing grease is prone to crusting and deterioration, and areas lacking sealing grease will remain in a state of constant lack of sealing grease. After crusting, the sealing grease not only loses its lubricating effect, but its solidified material will also cause dry friction with the sealing sheet 41, the axle 10, the wheel 20, and other structures, and may even act as abrasive particles to exacerbate wear, leading to decreased sealing performance and damage to the seal.

[0035] In this embodiment, by designing the first radial gap 51 and / or the second radial gap 52 as eccentric annular gaps, when the wheel 20 rotates relative to the axle 10, the gap width changes periodically along the circumference, and the gap volume also increases and decreases periodically accordingly. This volume change has a pumping and squeezing effect on the sealing grease within the gap, causing the sealing grease to continuously flow, stir, and redistribute within the gap, constantly replenishing the grease to the narrower gaps and areas prone to contact, thereby reducing the risk of long-term grease stagnation and crusting, keeping the friction pair surfaces constantly lubricated, and avoiding dry friction.

[0036] Preferably, in one embodiment, the first sealing plate 4101 and / or the second sealing plate 4102 are eccentric annular sealing plates, so that the first radial gap 51 and / or the second radial gap 52 form an eccentric annular gap. Here, an eccentric annular sealing plate means that the center of the inner ring of the annular sealing plate does not coincide with the center of the outer ring, that is, the radial width of the sealing plate is uneven along the circumferential direction, with one side being thicker and the other side thinner. Specifically, for the first sealing plate 4101 installed on the axle 10, the first radial gap 51 between its outer circumference and the wheel 20 will exhibit a distribution that is wider on one side and narrower on the other due to the eccentricity of the sealing plate; for the second sealing plate 4102 installed on the wheel 20, the second radial gap 52 between its inner circumference and the axle 10 will also form an eccentric annular gap with varying width. In other words, by setting the sealing plate 41 itself as an eccentric structure, the corresponding radial gap can be made to form an eccentric annular gap. By directly setting the first sealing plate 4101 and / or the second sealing plate 4102 as eccentric annular sealing plates, there are advantages in processing and manufacturing: since the eccentric structure only needs to be implemented on the independent part of the sealing plate 41, only the sealing plate 41 itself needs to be eccentrically machined to form the eccentric annular gap, without the need to modify the axle 10 or the wheel 20 to have an eccentric structure. The axle 10 and the wheel 20 can still maintain the conventional concentric rotation structure, and their processing technology and assembly standards do not need to be changed, which reduces the manufacturing difficulty and processing cost, and also facilitates the modification of the sealing structure and replacement of the sealing plates on the existing sintering trolley, which is conducive to improving the applicability and maintenance convenience of the sealing structure.

[0037] Preferably, in one embodiment, both the first sealing piece 4101 and the second sealing piece 4102 are eccentric annular sealing pieces, so that the first radial gap 51 and the second radial gap 52 form the eccentric annular gap. By setting both the first sealing piece 4101 and the second sealing piece 4102 as eccentric annular sealing pieces, the first radial gap 51 and the second radial gap 52 both form eccentric annular gaps. During the rotation of the wheel 20 relative to the axle 10, the widths of the two radial gaps change periodically along the circumference, and the gap volume increases and decreases periodically accordingly. This creates a pumping and squeezing effect on the sealing grease, causing it to continuously flow and redistribute throughout the labyrinthine sealing channel 50. The grease actively replenishes areas with narrower gaps and higher contact rates, effectively preventing grease from crusting and deteriorating due to prolonged stagnation. This reduces the risk of dry friction between crusted grease and the sealing sheet 41, axle 10, or wheel 20, ensuring good lubrication between the sealing sheet 41 and its mating surfaces. This further improves the sealing reliability and service life of the sealing structure under high temperature, high dust, and long-term operating conditions. Furthermore, since the eccentric structure only requires machining on the sealing sheet 41 (an independent part), eliminating the need for eccentric machining on the axle 10 and wheel 20, manufacturing difficulty and cost are reduced, facilitating the modification and maintenance of the sealing structure.

[0038] More preferably, in one embodiment, each of the sealing pieces 41 in the seal 40 is an eccentric annular sealing piece.

[0039] Preferably, in one embodiment, the sealing structure of the sintering trolley wheel further includes a retaining wheel 60, which is rotatably mounted on the axle 10 via a retaining wheel bearing 70. A retaining wheel seal 80 is provided between the retaining wheel 60 and the axle 10. Two sets of retaining wheel seals 80 are provided, with the two sets of retaining wheel seals 80 located on opposite axial sides of the retaining wheel bearing 70. The retaining wheel seal 80 includes multiple retaining wheel seal pieces 81 arranged sequentially along the axial direction of the axle 10. Of two adjacent retaining wheel seal pieces 81, one is mounted on the axle 10 and the other is mounted on the retaining wheel 60, so that the multiple retaining wheel seal pieces 81 form a labyrinth-type retaining wheel sealing channel 90 in the space between the axle 10 and the retaining wheel 60. The retaining wheel sealing channel 90 is filled with sealing grease.

[0040] In the sintering trolley, the wheels 20 are used to support the trolley and move along the track, bearing the weight of the trolley and providing rolling operation; while the chuck 60 is used to cooperate with transmission or guiding components such as star wheels on the sintering machine. Both are rotatably mounted on the same axle 10 and supported by the bearing 30 and the chuck bearing 70, respectively. Since the chuck 60 is also in a high-temperature, high-dust operating environment, its bearing part also faces problems such as dust intrusion, loss of sealing grease, and dry friction.

[0041] This embodiment includes the chuck 60 within the sealing protection range. Two sets of chuck seals 80 are installed between the chuck 60 and the axle 10, employing the same stacked labyrinth seal structure as the wheel seal. The staggered chuck seal plates 81 form a labyrinth seal channel 90 between the axle 10 and the chuck 60, filled with sealing grease. This structural design effectively seals both axial sides of the chuck bearing 70, significantly increasing the flow resistance of external dust entering the bearing cavity, preventing grease loss, and avoiding dry friction and abrasive wear between the chuck seal plates 81 and the axle 10 or chuck 60. This extends the service life of the chuck bearing 70, the chuck 60, and the entire sintering trolley, improving equipment reliability and economy. Furthermore, the wheel seal structure and the chuck seal structure use the same stacked labyrinth seal concept, facilitating unified design, processing, and replacement / maintenance, thus reducing manufacturing costs.

[0042] Currently, in other embodiments, a laminated seal may be used only at the wheel 20 (or the chuck 60), while a conventional sealing structure (e.g., a lip seal) may be used at the chuck 60 (or the wheel 20).

[0043] Preferably, in one embodiment, the chuck seal 81 installed on the axle 10 is a first chuck seal 8101, and the chuck seal 81 installed on the chuck 60 is a second chuck seal 8102. A first radial clearance 91 is provided between the outer periphery of the first chuck seal 8101 and the chuck 60, and a second radial clearance 92 is provided between the inner periphery of the second chuck seal 8102 and the axle 10. Adjacent first chuck seals 8101 and second chuck seals 8102 at least partially overlap radially, and an axial clearance 93 is provided between the overlapping portions. The axial clearance 93 communicates with the first radial clearance 91 and the second radial clearance 92, respectively, forming a tortuous labyrinthine chuck seal channel 90. Through this structural design, the radial clearance 91 of the first chuck, the axial clearance 93 of the chuck, and the radial clearance 92 of the second chuck are sequentially connected to form a tortuous labyrinthine chuck sealing channel 90. This significantly extends the path for external dust to enter the chuck bearing cavity, forcing the leaking medium to repeatedly zigzag along the radial and axial directions, greatly increasing the flow resistance. Even if a breathing effect occurs due to temperature fluctuations, external dust is less likely to directly intrude, thus effectively reducing the amount of dust inhaled. At the same time, gaps are left between each chuck sealing plate 81 and the chuck 60, the axle 10, and between adjacent chuck sealing plates 81, preventing direct contact and avoiding dry friction and abrasive wear. The sealing grease filled in this labyrinthine channel is not easily lost due to the tortuous channel, and can maintain lubrication for a long time, further ensuring the reliable operation of the chuck 60 and the chuck bearing 70, and extending the overall service life of the sintering trolley.

[0044] Preferably, in one embodiment, the radial clearance 91 of the first chuck and / or the radial clearance 92 of the second chuck are eccentric annular clearances. Similarly, by setting the radial clearance 91 of the first chuck (the radial clearance 92 of the second chuck) as an eccentric annular clearance, when the chuck 60 rotates relative to the axle 10, the clearance width changes periodically along the circumference, and the clearance volume also increases and decreases periodically. This volume change exerts a pumping and squeezing effect on the sealing grease within the clearance, causing the sealing grease to continuously flow, stir, and redistribute within the clearance, constantly replenishing the grease to the narrower, more easily contacted areas, thereby reducing the risk of long-term grease stagnation and crusting, keeping the friction pair surfaces consistently lubricated, and preventing dry friction.

[0045] Preferably, in one embodiment, both the first chuck seal 8101 and the second chuck seal 8102 are eccentric annular seals, so that the radial clearance 91 of the first chuck and the radial clearance 92 of the second chuck form an eccentric annular gap. Similarly, with this structural design, since the eccentric structure only needs to be machined on the independent part of the chuck seal 81, there is no need to perform eccentric machining on the axle 10 and the chuck 60, reducing manufacturing difficulty and cost, and facilitating the modification and maintenance of the sealing structure.

[0046] More preferably, in one embodiment, each of the caliper seal pieces 81 in the caliper seal 80 is an eccentric annular seal piece.

[0047] Understandably, lip seals in the current technology are made of rubber, and under long-term use, there is the problem of rubber aging. Usually, the lifespan of a lip seal is less than 3 years.

[0048] Preferably, in one embodiment, both the sealing sheet 41 and the caliper sealing sheet 81 are made of hardened heat-resistant metal, ceramic, or gold-ceramic composite material, which eliminates the problem of rubber aging and can operate stably for a long time in environments above 400°C. Meanwhile, in one embodiment, a sintering trolley wheel assembly 100 is also provided, which incorporates the sealing structure of the sintering trolley wheel.

[0049] Preferably, in one embodiment, the axle 10 is provided with an oil injection channel 11, which communicates with the labyrinth-type sealing channel 50. By providing the oil injection channel 11 in the axle 10 that communicates with the labyrinth-type sealing channel 50, new sealing grease can be directly injected into the labyrinth-type sealing channel 50 through the oil injection channel 11 without disassembling the wheel and sealing structure. The newly injected sealing grease can gradually squeeze out the old grease that has aged, deteriorated, or mixed with dust in the channel along the tortuous path of the labyrinth-type sealing channel 50, realizing online replenishment and replacement of sealing grease. This ensures that the sealing channel always maintains a good grease condition and lubrication performance, avoiding dry friction and sealing failure caused by grease crusting, loss, or performance degradation, further extending the service life of the sealing structure, wheel, and sintering trolley, while reducing maintenance difficulty and downtime costs.

[0050] More preferably, in one embodiment, the oil injection channel 11 is also connected to the labyrinth caliper seal channel 90, thereby allowing the replacement of aged sealing grease in the labyrinth caliper seal channel 90.

[0051] Preferably, in one embodiment, the axle 10 includes an axle body 12, a bushing 13, and an adjusting member 14. The bushing 13 is sleeved on the axle body 12, and the adjusting member 14 is connected to one end of the axle body 12. Of the two sets of seals 40, one set of seals 40 is specifically disposed between the adjusting member 14 and the wheel 20, and the other set of seals 40 is specifically disposed between the bushing 13 and the wheel 20. The bearing 30 is disposed between the wheel 20 and the bushing 13.

[0052] More preferably, in one embodiment, the bushing 13 is an eccentric bushing, and the bushing 13 is fixed to the axle body 12 by the adjusting member 14. The adjusting member 14 is detachably fastened to one end of the axle body 12 by bolts. Here, an eccentric bushing refers to a bushing whose inner hole center and outer circle center are eccentrically positioned, so that after the bushing 13 is installed on the axle body 12, the rotation center of the wheel 20 is offset relative to the axis of the axle body 12. Since the bushing 13 is detachably fixed to the axle body 12 by the adjusting member 14, during assembly or maintenance, the adjusting member 14 can be loosened, and the rotation of the adjusting member 14 drives the bushing 13 to rotate, thereby changing its circumferential installation angle on the axle body 12, thus adjusting the offset direction of the outer circle center of the bushing 13 relative to the axis of the axle body 12, and thereby achieving adjustment of the height of the wheel 20. This design eliminates the need to replace wheels or axle components of different specifications. The wheel height can be flexibly adjusted based on the actual wear and tear of the sintering trolley or the condition of the track, ensuring good contact between the wheels and the track. This improves the stability of the trolley's operation, compensates for wear caused by long-term operation, reduces maintenance costs, and enhances the adaptability and operational reliability of the sintering trolley. Furthermore, when wheels experience uneven load distribution or even become suspended, the circumferential installation angle of the bushing 13 can be adjusted according to the degree of uneven load distribution or suspension. This allows the wheels to re-engage with the track or to achieve a more balanced force on each wheel, thus preventing uneven load distribution or suspension on one side of the wheel, reducing bearing uneven load and wear, and extending the service life of the wheels and the sintering trolley.

[0053] More preferably, in one embodiment, the adjusting member 14 is also detachably provided with an anti-loosening member 15, which is mainly used to prevent the bolts fastening the adjusting member 14 from loosening.

[0054] Preferably, in one embodiment, the wheel 20 includes a wheel body 21 and an end cap 22 disposed at one end of the wheel body 21, and a set of the sealing members 40 are specifically disposed between the end cap 22 and the adjusting member 14.

[0055] The above description is merely an embodiment of the present invention. It should be noted that those skilled in the art can make improvements without departing from the inventive concept of the present invention, but these improvements all fall within the protection scope of the present invention.

Claims

1. A sealing structure for a sintered trolley wheel, characterized in that, Including axles, wheels, and chucks; The wheel is rotatably mounted on the axle via bearings; The cam is rotatably mounted on the axle via a cam bearing; A seal is provided between the wheel and the axle. There are two sets of seals, and the two sets of seals are located on both sides of the axial direction of the bearing. A cam seal is provided between the cam and the axle. There are two sets of cam seals, and the two sets of cam seals are located on both sides of the axial direction of the cam. The sealing element includes multiple sealing plates arranged sequentially along the axial direction of the axle. In two adjacent sealing plates, one is installed on the axle and the other is installed on the wheel, so that the multiple sealing plates form a labyrinth-like sealing channel in the space between the axle and the wheel. The labyrinthine sealed channel is filled with sealing grease. And / or, the cam seal includes multiple cam seal pieces arranged sequentially along the axial direction of the axle, wherein one of two adjacent cam seal pieces is installed on the axle and the other is installed on the cam, so that the multiple cam seal pieces form a labyrinthine cam seal channel in the space between the axle and the cam; The sealing channel of the caliper is filled with sealing grease.

2. The sealing structure of the sintered trolley wheel according to claim 1, characterized in that, When the sealing element includes multiple sealing sheets arranged sequentially along the axial direction of the axle, the sealing sheet installed on the axle is the first sealing sheet, and the sealing sheet installed on the wheel is the second sealing sheet; A first radial gap is left between the outer periphery of the first sealing sheet and the wheel; A second radial gap is left between the inner circumference of the second sealing sheet and the axle; The adjacent first and second sealing pieces overlap at least partially in the radial direction, and there is an axial gap between the overlapping portions. The axial gap communicates with the first radial gap and the second radial gap respectively, forming a tortuous labyrinthine sealing channel.

3. The sealing structure of the sintering trolley wheel according to claim 2, characterized in that, The first radial gap and / or the second radial gap are eccentric annular gaps.

4. The sealing structure of the sintered trolley wheel according to claim 3, characterized in that, The first sealing sheet and / or the second sealing sheet are eccentric annular sealing sheets, so that the first radial gap and / or the second radial gap form an eccentric annular gap.

5. The sealing structure of the sintered trolley wheel according to claim 4, characterized in that, Both the first sealing sheet and the second sealing sheet are eccentric annular sealing sheets, so that the first radial gap and the second radial gap form the eccentric annular gap.

6. The sealing structure of the sintered trolley wheel according to claim 1, characterized in that, When the cam seal includes multiple cam seal pieces arranged sequentially along the axial direction of the axle, the cam seal piece installed on the axle is the first cam seal piece, and the cam seal piece installed on the cam is the second cam seal piece; A radial clearance is provided between the outer periphery of the first caliper sealing plate and the caliper; A radial clearance of the second cam seal is provided between the inner circumference of the second cam seal and the axle. The adjacent first and second chuck seals overlap at least partially in the radial direction, and there is an axial gap between the overlapping portions. The axial gap of the chuck communicates with the radial gaps of the first and second chucks respectively, forming a tortuous labyrinthine chuck sealing channel.

7. The sealing structure of the sintered trolley wheel according to claim 6, characterized in that, The radial clearance of the first caliper and / or the radial clearance of the second caliper are eccentric annular clearances.

8. The sealing structure of the sintered trolley wheel according to claim 7, characterized in that, Both the first and second caliper seals are eccentric annular seals, so that the radial clearance of the first caliper and the radial clearance of the second caliper form an eccentric annular gap.

9. A sintered trolley wheel assembly, characterized in that, The application has a sealing structure for the sintered trolley wheels as described in any one of claims 1 to 8.

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