An axial sealing ring for high-speed wheel axles

Abstract

This invention relates to the field of axial sealing technology, specifically to an axial sealing ring for high-speed wheel axles. The axial sealing ring for high-speed wheel axles provided by this invention includes a hub, a ring body, and a wheel axle, all coaxially arranged. The ring body is installed between the inner surface of the hub and the outer surface of the wheel axle. A shaft groove is formed on the outer surface of the wheel axle, and the ring body is fitted into the shaft groove. The ring body is annular, and a Z-shaped break is formed on its side that completely penetrates the ring body. The rotation of the wheel axle drives the ring body to rotate, and the resulting centrifugal force overcomes the inherent elasticity of the sealing ring and its friction with the shaft groove. Simultaneously, due to the presence of the Z-shaped break, the ring body undergoes radial deformation, effectively increasing the contact pressure between the sealing ring and the shaft groove, thereby reducing the gap between the ring body and the hub, resulting in a better sealing effect. Furthermore, the structure is simple and the manufacturing cost is low.

Description

Technical Field

[0001] This invention relates to the field of axial sealing technology, and more specifically to an axial sealing ring for high-speed wheel axles. Background Technology

[0002] Currently, the commonly used axial sealing forms at home and abroad mainly include gasket seals, labyrinth seals, packing seals, mechanical seals and spiral seals. The commonly used sealing forms for high-speed or ultra-high-speed rotating structures are labyrinth seals and mechanical seals.

[0003] A labyrinth seal generally consists of several sequentially arranged annular sealing teeth around the axle. These teeth form a series of flow-blocking gaps and expansion cavities. The sealed medium experiences a throttling effect as it passes through the gaps in the labyrinth, thus preventing leakage. The mechanism by which fluid encounters resistance and reduces its flow rate when passing through a labyrinth is called the "labyrinth effect." For liquids, there are fluid dynamic effects, including hydraulic friction and flow contraction; for gases, there are thermodynamic effects, namely the heat transfer caused by compression or expansion within the labyrinth; in addition, there is the "permeability effect," etc. The labyrinth effect is a comprehensive reaction of these effects, making the mechanism of a labyrinth seal very complex.

[0004] Mechanical seals generally refer to devices that prevent fluid leakage, consisting of at least one pair of end faces perpendicular to the axis of the rotating wheel, which are kept in contact and slide relative to each other under the action of fluid pressure and the elastic force (or magnetic force) of the compensation mechanism, as well as the cooperation of auxiliary seals. Common mechanical seal structures consist of components such as a stationary ring, a rotating ring, an elastic element spring seat, a set screw, a rotating ring auxiliary sealing ring, and a stationary ring auxiliary sealing ring. Anti-rotation pins are fixed on the gland to prevent the stationary ring from rotating.

[0005] However, both mechanical seals and labyrinth seals have relatively complex structures and high manufacturing costs. Summary of the Invention

[0006] (I) The problem to be solved by the present invention is that traditional mechanical seals or labyrinth seals have relatively complex structures and high manufacturing costs.

[0007] (II) Technical Solution

[0008] An axial sealing ring for a high-speed wheel axle includes a hub, a ring body, and a wheel axle, wherein the hub, the ring body, and the wheel axle are coaxially arranged.

[0009] The ring is installed between the inner side of the hub and the outer side of the axle;

[0010] A shaft groove is formed on the outer side of the axle, and the ring body is fitted inside the shaft groove;

[0011] The ring is circular, and a Z-shaped cut is provided on the side of the ring that completely penetrates the ring.

[0012] According to one embodiment of the present invention, a first circumferential gap is formed between the inner side surface of the ring body and the inner side surface of the shaft groove, and a second circumferential gap is formed between the outer side surface of the ring body and the inner side surface of the hub.

[0013] According to one embodiment of the present invention, the ring body has a first side end face and a second side end face facing each other, a first contact gap is formed between the first side end face of the ring body and the inner top wall of the shaft groove, and a second contact gap is formed between the second side end face of the ring body and the inner bottom wall of the shaft groove.

[0014] According to one embodiment of the present invention, the Z-shaped fracture includes a first fracture, a second fracture, and a third fracture that are connected in sequence;

[0015] Both the first fracture and the third fracture are parallel to the axis of the ring body. The first fracture extends from the first side end face of the ring body toward the second side end face, and the second fracture extends from the second side end face of the ring body toward the first side end face.

[0016] According to one embodiment of the present invention, the second fracture has a first inclined surface and a second inclined surface, wherein the projection of the first inclined surface on a plane containing the axis of the ring body forms an angle with the axis.

[0017] According to one embodiment of the present invention, the first inclined plane and the second inclined plane are parallel, or the first inclined plane and the second inclined plane intersect.

[0018] According to one embodiment of the present invention, the first fracture has a first cross-section and a third cross-section, the first cross-section and the third cross-section being parallel, or the first cross-section and the third cross-section intersecting.

[0019] According to one embodiment of the present invention, the third fracture has a second cross-section and a fourth cross-section, the second cross-section and the fourth cross-section being parallel, or the second cross-section and the fourth cross-section intersecting.

[0020] According to one embodiment of the present invention, the height of the first fracture is less than half the thickness of the ring body, and the height of the third fracture is less than half the thickness of the ring body.

[0021] According to one embodiment of the present invention, the included angle ranges from 84° to 89°.

[0022] The beneficial effects of this invention are:

[0023] This invention provides an axial sealing ring for high-speed wheel axles, comprising: a hub, a ring body, and a wheel axle, all coaxially arranged. The ring body is installed between the inner side of the hub and the outer side of the wheel axle. A shaft groove is formed on the outer side of the wheel axle, and the ring body is fitted into the shaft groove. The ring body is circular, and a Z-shaped break is formed on its side that completely penetrates the ring body. The rotation of the wheel axle drives the ring body to rotate, and the resulting centrifugal force overcomes the inherent elasticity of the sealing ring and its friction with the shaft groove. Simultaneously, due to the presence of the Z-shaped break, the ring body undergoes radial deformation, increasing its diameter and effectively increasing the contact pressure between the sealing ring and the shaft groove. This reduces the gap between the ring body and the hub, resulting in a better sealing effect. Furthermore, the structure is simple and the manufacturing cost is low. Attached Figure Description

[0024] To more clearly illustrate the specific embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the specific embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of the present invention. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0025] Figure 1 This is a structural diagram of the wheel hub after part of it has been removed, as provided in an embodiment of the present invention.

[0026] Figure 2 This is a structural diagram of the ring provided in an embodiment of the present invention;

[0027] Figure 3 A cross-sectional view provided for an embodiment of the present invention;

[0028] Figure 4 Provided by the present invention Figure 1 Top view.

[0029] Icons: 1-Hub; 2-Axle; 3-Ring; 301-First cross-section; 302-First inclined surface; 303-Second cross-section; 4-First circumferential gap; 5-First contact gap; 6-Second contact gap; 7-Second circumferential gap. Detailed Implementation

[0030] The technical solution of the present invention will be clearly and completely described below with reference to the embodiments. 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.

[0031] like Figures 1-4 As shown, Figure 1This is an assembly drawing of hub 1, ring 3, and axle 2, but part of hub 1 has been cut off. Figure 2 The diagram shows the structure of the ring body 3. One embodiment of the present invention provides an axial sealing ring for a high-speed wheel axle, including a hub 1, a ring body 3 and a wheel axle 2. The hub 1, the ring body 3 and the wheel axle 2 are coaxially arranged, and the ring body 3 is a piston ring.

[0032] Among them, the inner diameter of the hub 1 is larger than the outer diameter of the sealing ring, the outer diameter of the sealing ring is larger than the outer diameter of the axle 2, and the ring body 3 is installed between the inner side of the hub 1 and the outer side of the axle 2.

[0033] A shaft groove is provided on the outer side of the axle 2. The shaft groove is an annular groove, and the ring body 3 is nested in the shaft groove.

[0034] The ring 3 is circular, and a Z-shaped cut is provided on the side of the ring 3 that completely penetrates the ring 3.

[0035] In this embodiment, as Figure 2 As shown, the ring 3 has opposing first and second side end faces, wherein, from Figure 2 See, the first side end face is the upper surface of the ring 3, the second side end face is the lower surface of the ring 3, and the Z-shaped fracture includes the first fracture, the second fracture and the third fracture connected in sequence.

[0036] Both the first and third fractures are parallel to the axis of the ring 3. The first fracture extends from the first side end face of the ring 3 toward the second side end face, and the second fracture extends from the second side end face of the ring 3 toward the first side end face. The second fracture extends from the lower end of the first fracture to the upper end of the third fracture.

[0037] Furthermore, the first fracture extends from the upper surface of the ring 3 to a position close to the middle of the ring 3, that is, the height of the first fracture is less than half the thickness of the ring 3. Similarly, the height of the third fracture is less than half the thickness of the ring 3.

[0038] Optionally, the height of the first fracture is the same as the height of the third fracture.

[0039] In this embodiment, as Figure 2 As shown, the first fracture has a first cross-section 301 and a third cross-section, the second fracture has a first inclined surface 302 and a second inclined surface, and the third fracture has a second cross-section 303 and a fourth cross-section.

[0040] The first section 301, the first inclined surface 302, and the second section 303 are sequentially connected to form two steps. The first section 301 forms a step with the upper surface of the ring 3, and the first inclined surface 302 forms a step with the second section 303. The first section 301 and the second section 303 are parallel. Figure 2From the perspective of the first section 301, the first inclined surface 302 and the second section 303 are connected in sequence to form a lying Z shape;

[0041] Among them, the third section, the second inclined section and the fourth section are connected in sequence, forming two steps. The third section and the upper surface of the ring 3 form a step, the second inclined section and the fourth section form a step, and the third section and the fourth section are parallel.

[0042] As a specific embodiment, such as Figure 3 and Figure 1 As shown, a first circumferential gap 4 is formed between the inner side surface of the ring body 3 and the inner side surface of the shaft groove, a second circumferential gap 7 is formed between the outer side surface of the ring body 3 and the inner side surface of the hub 1, a first contact gap 5 is formed between the first side end face of the ring body 3 and the inner top wall of the shaft groove, and a second contact gap 6 is formed between the second side end face of the ring body 3 and the inner bottom wall of the shaft groove.

[0043] like Figure 3 As shown, when the axle 2 is stationary, the ring 3 is held in the axle groove by its inherent elasticity. At this time, the first circumferential gap 4 is small, which can provide friction between the ring 3 and the axle 2. A second circumferential gap 7 is formed between the outer side of the ring 3 and the inner side of the hub 1. The width of the second circumferential gap 7 is sufficient to make there no friction between the outer side of the ring 3 and the inner side of the hub 1. At the same time, there is no friction between the first side end face of the ring 3 and the inner top wall of the axle groove, and there is no friction between the second side end face of the ring 3 and the inner bottom wall of the axle groove.

[0044] When the wheel axle 2 rotates, the friction between the inner surface of the ring body 3 and the inner surface of the shaft groove causes the ring body 3 to rotate synchronously with the wheel axle 2, generating centrifugal force. Since the Z-shaped break breaks the ring body 3, both ends of the ring body 3 are free ends. Under the action of centrifugal force, the ring body 3 expands radially, causing the width of the first circumferential gap 4 between the inner surface of the ring body 3 and the inner surface of the shaft groove to increase until there is no longer any contact between the inner surface of the ring body 3 and the inner surface of the shaft groove, and it can no longer provide friction.

[0045] However, under the action of centrifugal force, the ring 3 at the Z-shaped fracture point undergoes circumferential displacement. That is, the ring 3 near the Z-shaped fracture point expands radially under the action of centrifugal force. This increases the contact area between the upper surface of the ring 3 and the top wall of the shaft groove, and the contact area between the lower surface of the ring 3 and the bottom wall of the shaft groove. As a result, the ring 3 and the shaft groove exert contact pressure, thus achieving synchronous rotation of the ring 3 and the wheel axle 2.

[0046] That is, as the axle 2 rotates, the friction at the first circumferential gap 4 gradually disappears. As the rotational speed of the axle 2 increases, the expansion dimension of the sealing ring increases, and the axial thickness at the Z-shaped fracture contact position increases. This causes the friction between the upper surface of the sealing ring and the top wall of the shaft groove, and the friction between the lower surface of the sealing ring and the bottom wall of the shaft groove, to gradually increase. After reaching a certain rotational speed, this friction can balance the centrifugal force generated by the increased rotational speed, that is, the sealing ring is in a locked state. This reduces the size of the second circumferential gap 7, increases the sealing effect between the sealing ring and the hub 1, and ensures that there is a certain gap between the two to prevent dry friction.

[0047] According to a specific embodiment, the projection of the first inclined surface 302 onto a plane containing the axis of the ring body 3 forms an angle with the axis. Specifically, as shown in the example... Figure 4 As shown, from the cross-sectional view of AA, which is the plane containing the axis, the projection of the first inclined plane 302 onto the cross-section of AA forms an angle with the axis of the ring body 3 on the cross-section of AA. This angle ranges from 84° to 89°. Furthermore, the specific value of this angle varies according to the linear velocity of the wheel axle 2.

[0048] Specifically, given that the dimensions of the sealing ring and its associated structure, as well as the working environment, are known, the bending stiffness of the sealing ring can be determined using known conditions. This allows us to obtain the relationship between the tilt angle and the rotational speed, and the rationality of the setting can be verified through experiments.

[0049] After multiple experiments, it was found that when the surface linear velocity of wheel axle 2 is between 60 and 90 m / s, the angle between the first inclined surface 302 and the axis is between 88° and 89°.

[0050] When the surface linear velocity of wheel axle 2 is between 90 and 120 m / s, the angle between the first inclined surface 302 and the axis is between 86° and 88°. When the surface linear velocity of wheel axle 2 is between 120 and 160 m / s, the angle between the first inclined surface 302 and the axis is between 84° and 86°.

[0051] According to a specific embodiment, the first inclined plane 302 and the second inclined plane are parallel, while the first cross-section 301 and the third cross-section are parallel, and the second cross-section 303 and the fourth cross-section are parallel.

[0052] Optionally, the first section 301 and the third section intersect, the first inclined section 302 and the second inclined section are parallel, and the second section 303 and the fourth section are parallel. In this case, the first fracture is notched.

[0053] Optionally, the first section 301 and the third section are parallel, the first inclined surface 302 and the second inclined surface intersect, and the second section 303 and the fourth section are parallel.

[0054] Optionally, the first inclined plane 302 and the second inclined plane are parallel, and the first cross-section 301 and the third cross-section are parallel. However, at this time, the second cross-section 303 and the fourth cross-section intersect, that is, the third fracture is notched.

[0055] Working principle: As the rotational speed of wheel axle 2 increases, the expansion dimension of the sealing ring increases, and the axial thickness of the Z-shaped fracture contact position increases. This causes the friction between the upper surface of the sealing ring and the top wall of the shaft groove and the friction between the lower surface of the sealing ring and the bottom wall of the shaft groove to gradually increase. This can effectively increase the contact pressure between the sealing ring and the shaft groove. After reaching a certain rotational speed, this friction can balance the centrifugal force generated by the increased rotational speed, so as to ensure that the sealing ring and wheel axle 2 rotate synchronously.

[0056] The centrifugal force provided by the rotating wheel axle 2 and the sealing ring can overcome the inherent elasticity of the sealing ring and its contact friction with the shaft groove. As the rotation speed increases, its flare continuously increases until the force balance is reached. This process increases the diameter of the piston ring to a certain extent, making the gap between it and the wheel hub 1 smaller and improving the sealing effect.

[0057] Traditional labyrinth seals or mechanical avoidance systems are complex in structure, have high manufacturing costs, and occupy a large amount of axial and radial dimensions, thus limiting their application range.

[0058] Compared to traditional mechanical seals or labyrinth seals, this sealing method uses the rotation of the wheel shaft 2 to drive the sealing ring to rotate. The resulting centrifugal force is used to overcome the inherent elasticity of the sealing ring and its friction with the shaft groove, causing radial deformation. This increases the diameter of the piston ring, effectively reducing the gap between the piston ring and the wheel hub 1, resulting in a better sealing effect. Furthermore, it has a simple structure, low manufacturing cost, and occupies a smaller axial and radial dimension, making it more widely applicable.

[0059] In the description of this invention, it should be noted that the terms "upper" and "lower," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing the invention and 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, and therefore should not be construed as a limitation of the invention. Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0060] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linkage" 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 a connection within two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances. Furthermore, in the description of this invention, unless otherwise stated, "a plurality of" means two or more.

[0061] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. 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. An axial sealing ring for high-speed wheel axles, characterized in that, It includes a hub (1), a ring body (3) and axle (2), wherein the hub (1), the ring body (3) and the axle (2) are coaxially arranged; The ring (3) is installed between the inner side of the hub (1) and the outer side of the axle (2); A shaft groove is provided on the outer surface of the axle (2), and the ring (3) is fitted inside the shaft groove; The ring (3) is circular, and the side of the ring (3) is provided with a Z-shaped cut that completely penetrates the ring (3); The Z-shaped fracture includes a first fracture, a second fracture, and a third fracture that are connected in sequence. The first fracture and the third fracture are both parallel to the axis of the ring. The first fracture extends from the first side end face of the ring towards the second side end face, and the third fracture extends from the second side end face of the ring towards the first side end face. The second fracture extends from the lower end of the first fracture to the upper end of the third fracture, and the end of the first fracture away from the second fracture penetrates the ring. The end of the third fracture away from the second fracture also penetrates the ring. There is a first circumferential gap between the inner side surface of the ring body and the inner side surface of the shaft groove, a second circumferential gap between the outer side surface of the ring body and the inner side surface of the hub, a first contact gap between the first side end face of the ring body and the inner top wall of the shaft groove, and a second contact gap between the second side end face of the ring body and the inner bottom wall of the shaft groove. When the axle rotates, the first circumferential gap creates friction between the inner surface of the ring and the inner surface of the shaft groove, causing the ring to rotate synchronously with the axle. Simultaneously, the rotation of the ring generates centrifugal force, causing the ring to expand radially, thus increasing the first circumferential gap and decreasing the second circumferential gap, until the larger first circumferential gap eliminates contact between the inner surface of the ring and the inner surface of the shaft groove. As the axle's rotational speed increases, the expansion dimension of the sealing ring increases, and the axial thickness at the Z-shaped fracture contact position increases. This causes the friction between the upper surface of the sealing ring and the top wall of the shaft groove, and the friction between the lower surface of the sealing ring and the bottom wall of the shaft groove, to gradually increase. This friction balances the centrifugal force generated by the increased rotational speed, ensuring that the sealing ring rotates synchronously with the axle. The second fracture has a first inclined surface (302) and a second inclined surface, and the projection of the first inclined surface (302) onto a plane containing the axis of the ring body (3) forms an angle with the axis.

2. The axial sealing ring for high-speed wheel axles according to claim 1, characterized in that, The first inclined plane (302) and the second inclined plane are parallel, or the first inclined plane (302) and the second inclined plane intersect.

3. The axial sealing ring for high-speed wheel axles according to claim 1, characterized in that, The first fracture has a first cross-section (301) and a third cross-section, the first cross-section (301) and the third cross-section are parallel, or the first cross-section (301) and the third cross-section intersect.

4. The axial sealing ring for high-speed wheel axles according to claim 1, characterized in that, The third fracture has a second cross-section (303) and a fourth cross-section, the second cross-section (303) and the fourth cross-section being parallel, or the second cross-section (303) and the fourth cross-section intersecting.

5. An axial sealing ring for high-speed wheel axles according to claim 1, characterized in that, The height of the first fracture is less than half the thickness of the ring (3), and the height of the third fracture is less than half the thickness of the ring (3).

6. An axial sealing ring for high-speed wheel axles according to claim 1, characterized in that, The included angle ranges from 84° to 89°.

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