A shuttleless wheel door ring assembly and a shuttleless wheel circular weaving machine

Abstract

This utility model discloses a shuttleless shuttle frame assembly, belonging to the field of plastic weaving, which solves the problem of instability during the circular motion of a shuttleless shuttle. The technical solution mainly includes a shuttleless shuttle, an upper frame, a lower frame, and support rollers connecting the upper and lower frames. Multiple support rollers are distributed circumferentially along the frame assembly, forming a circular track for the shuttleless shuttle to run on. The outer circumferential side of the support rollers has a concave limiting groove with an upper limiting surface and a lower limiting surface. The shuttle bottom plate of the shuttleless shuttle has protruding limiting protrusions that extend into the limiting grooves and contact the upper and lower limiting surfaces respectively to achieve vertical limiting. There is a gap between the bottom surface of the shuttle bottom plate on both sides of the limiting protrusions and the outer circumferential side of the support rollers. This utility model is mainly used to effectively constrain the vertical displacement of the shuttle and improve operational stability. This utility model also provides a shuttleless circular loom using the above-mentioned shuttleless shuttle frame assembly.

Description

Technical Field

[0001] This utility model relates to plastic weaving machinery, and in particular to a shuttleless door ring assembly and a shuttleless circular loom. Background Technology

[0002] Existing technology CN220099311U discloses a shuttleless circular loom gate ring for cooperating with the shuttle. It includes two gate rings with multiple roller assemblies disposed between them. Each roller assembly includes a support shaft mounted between the two gate rings and two rollers rotatably mounted on the support shaft. The two rollers are symmetrically arranged. Each roller includes a radial support section and an axial support section in the axial direction. The shuttle has two symmetrically arranged support flanges. The outer circumferential surface of the radial support section of the roller is in contact with the outer side of the shuttle, and the axial support section of the roller is in contact with the corresponding support flange on the shuttle. By adopting the above technical solution, when the rollers cooperate with the shuttle, the outer circumferential surface of the radial support section of the roller is in contact with the outer side of the shuttle to provide radial support for the shuttle, and the axial support section of the roller is in contact with the corresponding support flange on the shuttle to provide axial support for the shuttle. This allows the shuttle to rotate smoothly in the circumferential direction, preventing it from swaying up and down during movement, thus ensuring the good quality of the woven product.

[0003] However, in the aforementioned prior art, the large gap between the two rollers, coupled with their separate assembly, results in a lack of effective constraint on the shuttle in the vertical direction. This leads to a tendency for the shuttle to float, making it difficult to control the accuracy of its height position and the precision of the spacing between them. Particularly during high-speed operation, the shuttle exhibits significant vertical bouncing, severely impacting weaving quality and equipment stability. The existing roller-shuttle coupling method makes it difficult to precisely control the shuttle's vertical displacement, resulting in uneven warp tension during weaving and making the fabric surface prone to defects. Furthermore, the traditional roller assembly is prone to wear after prolonged use, further exacerbating the shuttle's instability. Utility Model Content

[0004] The purpose of this invention is to provide a shuttleless gate ring assembly that solves the problem of instability of shuttleless shuttle boats during circular motion, and has the advantages of effectively constraining the vertical displacement of the shuttle and improving operational stability.

[0005] To achieve the above objectives, the present invention adopts the following technical solution: a shuttleless door ring assembly, comprising a shuttleless shuttle boat, an upper door ring, a lower door ring, and support rollers connecting the upper and lower door rings. Multiple support rollers are distributed circumferentially along the door ring assembly to form a circular track for the shuttleless shuttle boat to run. The outer circumferential side of the support rollers is provided with a concave limiting groove, which has an upper limiting surface and a lower limiting surface. The shuttle bottom plate of the shuttleless shuttle boat is provided with an outwardly protruding limiting protrusion. The limiting protrusion extends into the limiting groove and contacts and matches the upper and lower limiting surfaces respectively to achieve vertical limiting. There is a gap between the bottom surface of the shuttle bottom plate on both sides of the limiting protrusion and the outer circumferential side of the support rollers.

[0006] The present invention has the following advantages when adopting the above technical solution: This technical solution achieves vertical positioning through the synergistic action of the support rollers and the shuttle base plate. The support rollers are circumferentially distributed to form a circular track, providing a running foundation for the shuttleless shuttle. A concave limiting groove is provided on the outer circumferential side of the support rollers, and its upper and lower limiting surfaces contact the rigid limiting protrusions of the shuttle base plate, directly constraining the vertical displacement of the shuttle. The double-sided contact structure of the limiting protrusions embedded in the limiting grooves can simultaneously resist vertical movement. The shuttle base plate maintains a gap with the support rollers on both sides of the limiting protrusions, avoiding frictional wear in non-contact areas. This design, through a rigid limiting structure and gap fit, achieves precise vertical positioning while reducing running resistance, thereby solving the shuttle jump problem.

[0007] Furthermore, the outer periphery of the support roller is provided with a recessed section, and a wear-resistant flexible sleeve is fitted around the outer periphery of the recessed section. A limiting groove is provided on the outer periphery side of the wear-resistant flexible sleeve, and the limiting protrusion is a rigid protrusion that abuts against the outer periphery side of the wear-resistant flexible sleeve.

[0008] Using the aforementioned technical solution, the recessed section refers to the annular groove structure set on the outer periphery of the supporting roller, which can be achieved by turning. The depth and width of the recessed section are determined according to the installation requirements of the wear-resistant flexible sleeve, providing a stable assembly space for the wear-resistant flexible sleeve. The wear-resistant flexible sleeve is an annular sleeve body made of elastic material, which can be made of polyurethane or rubber through injection molding. Its inner diameter matches the outer diameter of the recessed section and is fixed by interference fit, forming a buffer layer at the rigid contact interface. The limiting groove is a continuous groove formed on the outer periphery of the wear-resistant flexible sleeve, which can be integrally formed with the wear-resistant flexible sleeve through molding. Its groove wall angle is adapted to the shape of the limiting protrusion, constraining the shuttle's movement trajectory in the vertical direction while allowing the wear-resistant flexible sleeve to undergo elastic deformation. The rigid protrusion is a metal boss structure extending outward on the shuttle bottom plate, which can be formed by welding or machining. Its surface hardness is higher than that of the wear-resistant flexible sleeve material, maintaining the geometric accuracy of the limiting structure during dynamic contact. Specifically, the recessed section is formed on the outer periphery of the support roller through machining, while the wear-resistant flexible sleeve is injection molded and precision-machined to form a composite structure, ensuring the concentricity of the support roller. When the shuttle is running, the rigid protrusion at its bottom is embedded in the limiting groove on the surface of the wear-resistant flexible sleeve, and the elastic deformation of the groove wall absorbs the vertical impact force generated by the shuttle's movement. Due to the damping characteristics of the wear-resistant flexible sleeve material, the vibration energy generated when the rigid protrusion contacts the groove wall is converted into heat energy and dissipated, avoiding direct collision between rigid components. At the same time, the wear-resistant properties of the wear-resistant flexible sleeve reduce the wear rate of the contact surface, and the geometry of the limiting groove maintains the stability of the limiting gap through elastic compensation. Compared with existing technologies, the traditional solution uses a fully rigid contact between the support roller and the shuttle, which leads to fatigue wear on the contact surface and cannot buffer impact loads. This solution transforms rigid contact into elastic contact by setting a recessed section on the surface of the support roller and assembling a wear-resistant flexible sleeve, absorbing impact energy through material deformation and reducing the coefficient of friction by utilizing the self-lubricating properties of the flexible material.

[0009] Furthermore, the angle between the upper limit surface and the lower limit surface is 60° to 160°.

[0010] Using the aforementioned technical solution, when the included angle of the limiting groove is within the range of 60° to 160°, a stable surface contact area is formed between the limiting protrusion and the limiting surface, and the contact area is dynamically adjusted with the angle. During shuttle operation, the vertical load is evenly transmitted to the support rollers through surface contact, avoiding accelerated wear caused by local stress concentration. At the same time, this angle range ensures that the opening width of the limiting groove is within a reasonable range, which can accommodate the movement trajectory of the limiting protrusion while limiting its vertical displacement amplitude, thereby suppressing the up-and-down floating of the shuttle.

[0011] Furthermore, the upper limit surface and the lower limit surface are symmetrical about the horizontal plane; and / or, the angle at which the lower limit surface is tilted downward relative to the horizontal plane is less than the angle at which the upper limit surface is tilted upward relative to the horizontal plane.

[0012] Using the aforementioned technical solution, the upper limit surface refers to the upper constraint surface located in the concave limiting groove on the outer circumference of the support roller, which contacts the limiting protrusion. Specifically, it can be implemented using an inclined plane or an arc surface. Its function is to limit the upward displacement of the shuttle through contact with the limiting protrusion. The lower limit surface refers to the lower constraint surface located in the concave limiting groove on the outer circumference of the support roller, which contacts the limiting protrusion. Specifically, it can be implemented using an inclined plane or an arc surface symmetrical to the upper limit surface. Its function is to limit the downward displacement of the shuttle through contact with the limiting protrusion. Horizontal symmetry means that the upper and lower limit surfaces are mirror-symmetrically distributed with respect to the horizontal plane passing through the axis of the support roller. This can be achieved by designing the two limit surfaces with the same inclination angle and symmetrical arrangement. Its function is to provide symmetrical constraint forces in the vertical direction for the limiting protrusion. Specifically, when the shuttleless shuttle is running, the limiting protrusion is embedded in the limiting groove, and its upper and lower surfaces contact the upper and lower limit surfaces, respectively. Because the two limiting surfaces are symmetrical about the horizontal plane, the constraint forces on the limiting protrusions in the vertical direction are symmetrically distributed, thus evenly suppressing the vertical displacement of the shuttle. When the shuttle tends to move vertically under the action of external forces, the symmetrical limiting surfaces convert the vertical offset into a tangential component force along the limiting surfaces through geometric constraints, thereby eliminating shuttle jump. Compared with existing technologies, the upper and lower limiting surfaces of the limiting groove in traditional solutions usually adopt an asymmetrical design or a single-plane constraint, resulting in an imbalance of the vertical constraint forces on the shuttle, which easily leads to floating. This solution, through a symmetrical limiting surface structure, enables the constraint forces to form a self-balancing mechanism in the vertical direction, significantly improving motion stability. Through the above technical solution, this application effectively suppresses vertical floating of the shuttle during operation, avoids shuttle tilting or track deviation caused by excessive constraint forces on one side, ensures that the limiting protrusions always move along the central plane of the limiting groove, thereby eliminating shuttle jump during weaving and ensuring the uniformity of fabric texture. Because the shuttle itself has weight, and the weft spindle is also important, the lower limit surface will bear a greater force. Therefore, in another embodiment, the angle of inclination of the lower limit surface relative to the horizontal plane downward can be designed to be smaller than the angle of inclination of the upper limit surface relative to the horizontal plane upward, which can better bear the weight and improve the stability of the shuttle's operation. To further improve the load-bearing capacity, the width of the lower limit surface can also be selected to be greater than the width of the upper limit surface.

[0013] Furthermore, the support roller includes a mandrel and an upper support sleeve, a limiting roller, and a lower support sleeve fitted on the mandrel. The upper support sleeve abuts between the upper door ring and the limiting roller, and the lower support sleeve abuts between the lower door ring and the limiting roller, thereby axially positioning the limiting roller.

[0014] In the aforementioned technical solution, the mandrel refers to a rigid rod-shaped component extending axially, which can be made of metal. It is used to support the installation of the upper support sleeve, the limiting roller, and the lower support sleeve, and provides basic support for axial positioning. The upper support sleeve is an annular component fitted onto the top of the mandrel, which can be made of wear-resistant material. It restricts the upward movement of the limiting roller by abutting against the space between the upper gate ring and the limiting roller. The lower support sleeve is an annular component fitted onto the bottom of the mandrel, which can be made of the same material as the upper support sleeve. It restricts the downward movement of the limiting roller by abutting against the space between the lower gate ring and the limiting roller. The limiting roller is a cylindrical component fitted into the middle of the mandrel, which can be a bearing or a rigid sleeve structure. It contacts the shuttle and provides rolling support, and its axial position is fixed by the bidirectional abutment of the upper and lower support sleeves. Specifically, the mandrel, as the core component for axial positioning, passes through the upper and lower gate rings, and the upper and lower support sleeves are respectively installed at both ends of the mandrel. During assembly, the upper support sleeve is pressed between the top of the mandrel and the limiting roller, while the lower support sleeve is pressed between the bottom of the mandrel and the limiting roller, forming a two-way clamping structure. This clamping method completely constrains the axial movement of the limiting roller, preventing roller position displacement due to gaps between the support sleeve and the limiting roller. Through the cooperation of the mandrel and the support sleeve, the installation spacing of the limiting rollers is precisely controlled, thereby eliminating vertical floating and jumping of the shuttle caused by excessive spacing of the roller assembly. Compared with the prior art, where two rollers are symmetrically installed on the support shaft with a fixed spacing, the roller spacing cannot be dynamically adjusted according to assembly errors or wear, resulting in insufficient vertical stability of the shuttle. This solution, through the axial positioning structure of the mandrel and the support sleeve, makes the installation position of the limiting roller adjustable and gapless, thereby reducing the roller spacing and maintaining rigid constraint, effectively suppressing vertical displacement during shuttle movement. Through the above technical solution, this application can accurately control the axial installation position of the limiting roller, eliminate the gap caused by assembly error or wear of the roller assembly, avoid vertical floating or jumping of the shuttle in the circumferential motion, ensure the stability of the shuttle running trajectory, and thus improve the weaving quality.

[0015] Furthermore, the limiting roller includes an embedded upper bearing and a lower bearing, the inner rings of the upper bearing and the lower bearing both mate with the spindle, the upper support sleeve extends into the top of the limiting roller and abuts against the inner ring of the upper bearing, and the lower support sleeve extends into the bottom of the limiting roller and abuts against the inner ring of the lower bearing.

[0016] In the aforementioned technical solution, the upper and lower bearings refer to two rolling bearings housed inside the limiting rollers. These can be implemented using deep groove ball bearings or angular contact bearings to reduce rotational friction resistance between the limiting rollers and the mandrel. The inner ring fit with the mandrel refers to an interference fit or transition fit between the bearing's inner ring and the mandrel, achieved through heat fitting or press fitting processes, keeping the bearing's inner ring and mandrel relatively stationary. The upper and lower support sleeves are annular parts fitted onto both ends of the mandrel, machined from metal, used to apply axial pressure to the bearing's inner ring. The support sleeve's end face forms rigid contact with the bearing's inner ring's end face, ensuring flatness through machining to eliminate gaps between the support sleeve and the bearing's inner ring. Specifically, after the bearing's inner ring is fixed to the mandrel, the limiting rollers achieve rotational freedom through the bearing's outer ring. The upper support sleeve presses downward against the upper bearing's inner ring, and the lower support sleeve presses upward against the lower bearing's inner ring, forming a bidirectional axial constraint. When the limiting roller is subjected to axial force, the inner ring of the bearing is restricted in its displacement by the support sleeve, preventing the bearing as a whole from moving along the mandrel. The fixed fit between the mandrel and the inner ring of the bearing ensures effective transmission of rotational torque, while the rigid contact between the support sleeve and the inner ring of the bearing forms an axial positioning reference. Compared with the prior art, in traditional structures, the roller is axially positioned only through a single-sided bearing or sliding sleeve, resulting in accumulated clearance and axial movement. This solution adopts a double-sided bearing with a bidirectional support sleeve structure, eliminating axial assembly clearance. The rigid contact between the inner ring of the bearing and the support sleeve forms double limiting, increasing the axial positioning stiffness by approximately 40%. Through the above technical solution, this application effectively suppresses the axial displacement of the limiting roller on the mandrel, controlling the axial movement of the roller to within 0.05 mm, and preventing the shuttle from jumping vertically due to roller movement. The rigid contact between the inner ring of the bearing and the support sleeve forms a stable axial constraint, while maintaining the rotational flexibility of the roller, reducing the shuttle's trajectory deviation to below 0.1 mm.

[0017] Furthermore, the top end of the mandrel extends upward to form an upper door ring, and the bottom end of the mandrel extends downward to form a lower door ring. The two ends of the mandrel are fixed by fasteners so that the upper and lower door rings clamp the limiting rollers to achieve axial positioning.

[0018] In the aforementioned technical solution, the mandrel refers to a rigid support shaft that runs through the upper and lower door rings and the limiting rollers. It can be made of high-strength alloy steel and is used to transmit axial clamping force and form a symmetrical constraint path. Fasteners are connecting components used to fix both ends of the mandrel, specifically a bolt and nut combination structure. Assembly gaps are eliminated by adjusting the preload. The upper and lower door rings refer to the upper and lower rigid frames that constitute the door ring assembly. Clamping force is applied by the fasteners at both ends of the mandrel, pressing the limiting rollers between them. Specifically, the top end of the mandrel extends upward and passes through the upper door ring, and the bottom end extends downward and passes through the lower door ring. Both ends are locked and fixed by bolts and nuts. When the fasteners are tightened, the upper and lower door rings are subjected to opposing forces, generating axial clamping force on the limiting rollers. Because both ends of the mandrel are rigidly fixed, the limiting rollers cannot move axially between the upper and lower door rings, thus eliminating displacement caused by installation gaps or dynamic loads. The symmetrical extension design of the mandrel ensures uniform distribution of clamping force, avoiding eccentric deformation caused by unilateral fixing. By adjusting the preload of the fasteners, the assembly tolerance between the support rollers and the gate ring can be further compensated, ensuring axial positioning accuracy. Compared with existing technologies, in traditional gate ring structures, the roller assembly achieves axial positioning only through single-sided fixing or partial clamping, which is prone to gaps due to vibration or wear, leading to changes in roller spacing. This solution forms a rigid axial constraint by extending the mandrel symmetrically at both ends and applying bidirectional clamping force, effectively suppressing the movement of the support rollers. At the same time, the preload adjustment actively eliminates assembly gaps, significantly improving axial positioning reliability. Through the above technical solution, this application can avoid changes in roller spacing caused by axial displacement of the support rollers during operation, thereby preventing vertical floating and jumping of the shuttle, ensuring smooth shuttle operation along the circumferential track, and improving the stability of weaving quality.

[0019] Furthermore, the wear-resistant flexible sleeve includes an upper ring body and a lower ring body. The recessed section includes an upper conical surface, a cylindrical surface and a lower conical surface from top to bottom. The upper ring body is fixed to the upper conical surface and at least covers a portion of the cylindrical surface downwards. An upper limit surface is provided on the upper ring body. The lower ring body is fixed to the lower conical surface and at least covers a portion of the cylindrical surface upwards. A lower limit surface is provided on the lower ring body.

[0020] Using the aforementioned technical solution, the upper ring refers to a split wear-resistant structure that covers the upper conical surface of the support roller and extends to the top of the cylindrical surface. Specifically, it can be fixed by injection molding rubber or polyurethane material to the upper conical surface and the cylindrical surface, followed by precision machining. The axial constraint force generated by the inclination angle of the conical surface enhances the contact stability between the upper ring and the support roller. The lower ring refers to a symmetrical split structure that covers the lower conical surface of the support roller and extends to the bottom of the cylindrical surface. Specifically, it can be fixed using the same material and process as the upper ring. The axial displacement of the lower ring is limited by the inclination angle of the lower conical surface, while simultaneously forming a bidirectional coverage of the cylindrical surface with the upper ring. The composite curved surface structure formed by the upper conical surface, the cylindrical surface, and the lower conical surface refers to the three-segment geometry of the recessed section of the support roller. Specifically, it can be formed into a continuously transitioning curved surface through machining. The combination of the conical and cylindrical surfaces achieves precise positioning and stress dispersion of the wear-resistant flexible sleeve. Specifically, the upper ring is fixed to the upper conical surface and extends downwards to cover the top area of ​​the cylindrical surface. The axial force generated by the inclination angle of the conical surface prevents the upper ring from detaching upwards during shuttle operation, while simultaneously covering the cylindrical surface to increase the contact area and distribute vertical loads. The lower ring is symmetrically fixed to the lower conical surface and extends upwards to cover the bottom area of ​​the cylindrical surface. The reverse axial force generated by the inclination angle of the lower conical surface constrains the lower ring's downward displacement, forming a bidirectional covering of the cylindrical surface together with the upper ring, eliminating the risk of axial movement of the wear-resistant flexible sleeve during high-speed friction. The upper and lower limiting surfaces are independently set on the upper and lower rings, respectively. When a local area fails due to long-term wear, only the corresponding ring needs to be replaced to restore the limiting function, avoiding the need to replace the entire wear-resistant flexible sleeve. The composite curved surface structure allows the wear-resistant flexible sleeve to decompose the impact force into axial and radial components through the conical angle when subjected to vertical impact, reducing internal stress concentration and improving structural durability. Compared to existing technologies, traditional integral wear-resistant flexible sleeves are directly fitted onto cylindrical recessed sections, relying solely on friction to resist axial displacement. During high-speed operation, stress concentration can easily lead to sleeve movement or localized wear. This solution utilizes a split ring body and a composite curved surface, employing the axial constraint force generated by the conical surface to enhance the sleeve's fixation. Simultaneously, the bidirectional coverage of the cylindrical surface by the upper and lower ring bodies forms a mechanical limit, effectively suppressing axial displacement. Furthermore, the split structure allows for partial replacement of worn components, significantly reducing maintenance costs compared to complete replacement. Through the above technical solution, this application solves the problems of axial displacement and localized wear caused by structural instability in wear-resistant flexible sleeves. The synergistic effect of the split ring body and the composite curved surface ensures that the limiting groove and limiting protrusion maintain a precise fit over a long period, extending the service life of the wear-resistant flexible sleeve and maintaining the stability of the shuttle's trajectory. In another embodiment, the upper and lower ring bodies can also be integrally formed structures.

[0021] Furthermore, the vertical thickness of the upper ring body from the upper limit surface to the upper conical surface is not less than 3mm, and the vertical thickness of the lower ring body from the lower limit surface to the lower conical surface is not less than 3mm.

[0022] Using the aforementioned technical solution, the upper ring body refers to the annular component covering the upper conical surface of the support roller and extending downwards to the cylindrical surface. Specifically, it can be made of vulcanized rubber or polyurethane material combined with a metal skeleton, increasing its vertical thickness to enhance compressive strength. The lower ring body refers to the annular component covering the lower conical surface of the support roller and extending upwards to the cylindrical surface. It can use the same materials and processes as the upper ring body, ensuring rigid support through its vertical thickness. Specifically, the vertical thickness of the upper ring body is set to be no less than 3mm, allowing it to disperse contact stress with sufficient material volume when the shuttle's limiting protrusion is pressed downwards, preventing the limiting surface from sinking due to localized deformation. The vertical thickness of the lower ring body is also no less than 3mm. When the shuttle is subjected to an upward force, the lower ring body maintains the positional stability of the lower limiting surface through the structural rigidity formed by its thickness. At this thickness, the deformation of the wear-resistant flexible sleeve is controlled within the allowable range, thereby reducing vertical clearance changes caused by sleeve compression or wear. In some specific embodiments, the mating surface between the upper ring and the upper conical surface can be designed as a stepped structure to increase the contact area, and an adhesive layer can be provided between the lower ring and the lower conical surface to enhance the fixing effect. Compared with the prior art, the thickness of the wear-resistant flexible sleeve ring is not clearly defined in the prior art, which makes the material prone to creep or wear after long-term pressure, thus causing the shuttle to float vertically. This solution, by setting a minimum vertical thickness, not only ensures the deformation resistance of the ring itself, but also reduces the risk of stress concentration through optimized material volume distribution. Through the above technical solution, this application effectively suppresses the vertical floating phenomenon of the shuttle during operation caused by insufficient thickness of the wear-resistant flexible sleeve, maintains stable contact between the limiting protrusion and the limiting groove, and thus ensures the smooth movement of the shuttle along the circumferential track.

[0023] Furthermore, the diameter of the cylindrical surface is not less than 20 mm.

[0024] In the aforementioned technical solution, the cylindrical surface refers to the outer circumferential surface of the supporting roller that contacts the outer side of the shuttle. Specifically, it can be achieved by machining a cylindrical structure from metal materials, increasing the diameter of the cylindrical surface to enhance the radial support area. A diameter of not less than 20mm means that the maximum straight-line distance of the cylindrical surface cross-section reaches or exceeds this value. This can be achieved by increasing the outer diameter of the mandrel or adjusting the thickness of the wear-resistant flexible sleeve, ensuring that the roller assembly has sufficient bending stiffness and deformation resistance when bearing the load of the shuttle movement. Specifically, the setting of the cylindrical surface diameter directly affects the radial load-bearing capacity of the roller assembly. When the diameter increases, the contact area between the roller and the outer side of the shuttle increases accordingly, allowing the radial load to be evenly transmitted to the gate ring structure through a wider support surface. This design effectively disperses the local stress generated by the shuttle movement, preventing the support gap from widening due to roller deformation. Simultaneously, the increased cylindrical surface diameter provides sufficient space for machining the limiting groove, ensuring a stable matching relationship between the limiting protrusion and the limiting groove, thereby forming a more reliable constraint in the vertical direction. Compared to existing technologies, the cylindrical diameter of traditional roller assemblies is typically less than 20mm, resulting in insufficient radial support area. This makes them prone to elastic deformation during high-speed shuttle movement, exacerbating vertical float. This solution strengthens the structural rigidity of the roller assembly by limiting the lower limit of the cylindrical diameter, significantly suppressing the impact of roller spacing on shuttle float. Through this technical solution, this application enhances the radial support stability of the roller assembly, reduces vertical shuttle jump caused by excessive roller spacing, ensures the shuttle maintains a stable posture while running along the circumferential track, and thus improves the interlacing accuracy of warp and weft yarns during weaving.

[0025] This utility model also provides a shuttleless circular loom, including the shuttleless gate ring assembly described in any of the above technical solutions. Attached Figure Description

[0026] The present invention will be further described below with reference to the accompanying drawings: Figure 1 This is a schematic diagram of a shuttleless door ring assembly according to the present invention (the shuttle is not shown). Figure 2 This is a schematic diagram of the shuttle boat in a shuttleless door ring assembly according to the present invention; Figure 3 This is a schematic diagram of a shuttleless door ring assembly according to the present invention (the upper door ring is not shown). Figure 4 This is a cross-sectional schematic diagram of a shuttleless door ring assembly according to the present invention; Figure 5 This is a cross-sectional view of the limiting roller in a shuttleless door ring assembly according to this utility model; Figure 6 This is a cross-sectional schematic diagram of the shuttle bottom plate in a shuttleless door ring assembly according to this utility model. Detailed Implementation

[0027] To make the objectives, technical solutions, and advantages of the embodiments of this utility model clearer, the technical solutions of the embodiments of this utility model will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this utility model, and not all embodiments.

[0028] The terms "first," "second," etc. (if present) in the specification and claims of this utility model are used to distinguish similar objects, not to describe a specific order or sequence. Even if "second" is used before a technical feature for distinction, it does not necessarily imply the presence of "first." It should be understood that in this utility model, "comprising" and "having," and any variations thereof, are intended to cover non-exclusive inclusion. It should be understood that in this utility model, "multiple" refers to two or more. "And / or" is merely a description of the relationship between related objects, indicating that three relationships can exist. For example, X and / or Y can represent: X alone, X and Y simultaneously, and Y alone. The character " / " generally indicates that the preceding and following related objects are in an "or" relationship. "Containing X, Y, and Z," "Containing X, Y, and Z" means that all three X, Y, and Z are included; "Containing X, Y, or Z" means that one of X, Y, and Z is included; "Containing X, Y, and / or Z" means that any one, two, or three of X, Y, and Z are included.

[0029] The technical solution of this utility model will be described in detail below with specific embodiments. The following specific embodiments can be selected to be combined or substituted with each other according to the actual situation, and the same or similar concepts or processes may not be described again in some embodiments.

[0030] like Figures 1 to 6 As shown, this utility model provides a shuttleless door ring assembly, including a shuttleless shuttle boat 100, an upper door ring 200, a lower door ring 300, and support rollers 400 connected between the upper door ring 200 and the lower door ring 300. Multiple support rollers 400 are distributed circumferentially along the door ring assembly to form a circular track for the shuttleless shuttle boat 100 to run on. The outer peripheral side of the support rollers 400 is provided with a concave limiting groove 401, which has an upper limiting surface 402 and a lower limiting surface 403. The shuttle bottom plate 101 of the shuttleless shuttle boat 100 is provided with an outwardly protruding limiting protrusion 11. The limiting protrusion 11 extends into the limiting groove 401 and contacts and matches the upper limiting surface 402 and the lower limiting surface 403 respectively to achieve vertical limiting. A gap 102 exists between the bottom surface of the shuttle bottom plate 101 on both sides of the limiting protrusion 11 and the outer peripheral side of the support rollers 400.

[0031] This invention achieves vertical positioning through the synergistic action of the support rollers 400 and the shuttle base plate 101. The support rollers 400 are circumferentially distributed to form a circular track, providing the running foundation for the shuttleless shuttle 100. A concave limiting groove 401 is provided on the outer circumferential side of the support rollers 400. Its upper limiting surface 402 and lower limiting surface 403 contact the rigid limiting protrusion 11 of the shuttle base plate 101, directly constraining the vertical displacement of the shuttle. The double-sided contact structure of the limiting protrusion 11 embedded in the limiting groove 401 simultaneously resists vertical movement. The shuttle base plate 101 maintains a gap 102 with the support rollers 400 on both sides of the limiting protrusion 11, avoiding frictional loss in non-contact areas. This design, through the cooperation of the rigid limiting structure and the gap 102, achieves precise vertical positioning while reducing running resistance, thereby solving the shuttle jump problem. Since the support roller 400 is a single component, there is no assembly error. This avoids the tolerance amplification caused by manufacturing and assembly issues that exist in existing technologies. It helps ensure that the shuttle moves on a horizontal circular track and greatly improves operational stability.

[0032] Due to the limited space design of the door ring assembly, to avoid the support roller 400 having an excessively large diameter, in one embodiment, a recessed section 404 is provided on the outer periphery of the support roller 400. A wear-resistant flexible sleeve 41 is fitted around the outer periphery of the recessed section 404. A limiting groove 401 is provided on the outer peripheral side of the wear-resistant flexible sleeve 41, and a limiting protrusion 11 is a rigid protrusion that abuts against the outer peripheral side of the wear-resistant flexible sleeve 41. The recessed section 404 refers to the annular groove structure provided on the outer periphery of the support roller 400, which can be achieved by turning. The depth and width of the recessed section 404 are determined according to the installation requirements of the wear-resistant flexible sleeve 41, and are used to provide a stable assembly space for the wear-resistant flexible sleeve 41. The wear-resistant flexible sleeve 41 refers to an annular sleeve made of elastic material, which can be made of polyurethane or rubber material through injection molding. Its inner diameter matches the outer diameter of the recessed section 404 and is fixed by interference fit, and is used to form a buffer layer at the rigid contact interface. The limiting groove 401 refers to a continuous groove formed on the outer periphery of the wear-resistant flexible sleeve 41. Specifically, it can be integrally formed with the wear-resistant flexible sleeve 41 through a molding process. The groove wall angle matches the shape of the limiting protrusion 11, used to constrain the shuttle's movement trajectory in the vertical direction while allowing the wear-resistant flexible sleeve 41 to undergo elastic deformation. The rigid protrusion refers to a metal boss structure extending outward on the shuttle base plate 101. Specifically, it can be formed by welding or machining, and its surface hardness is higher than that of the wear-resistant flexible sleeve 41 material. It is used to maintain the geometric accuracy of the limiting structure during dynamic contact. Specifically, the recessed section 404 is formed on the outer periphery of the support roller 400 through machining. The wear-resistant flexible sleeve 41 is pressed into the recessed section 404 to form a composite structure. When the shuttle is running, the rigid protrusion at its bottom is embedded in the limiting groove 401 on the surface of the wear-resistant flexible sleeve 41, and the elastic deformation of the groove wall absorbs the vertical impact force generated by the shuttle's movement. Due to the damping characteristics of the wear-resistant flexible sleeve 41 material, the vibration energy generated when the rigid protrusion contacts the groove wall is converted into heat energy and dissipated, avoiding direct collision between rigid components. Simultaneously, the wear-resistant properties of the flexible sleeve 41 reduce the wear rate of the contact surface, and the geometry of the limiting groove 401 maintains the stability of the limiting gap through elastic compensation. Compared with existing technologies, the traditional solution uses a fully rigid contact between the support roller 400 and the shuttle, leading to easy fatigue wear on the contact surface and an inability to buffer impact loads. This solution transforms rigid contact into elastic contact by setting a recessed section 404 on the surface of the support roller 400 and assembling it with the wear-resistant flexible sleeve 41. This absorbs impact energy through material deformation and reduces the coefficient of friction by utilizing the self-lubricating properties of the flexible material.

[0033] Since the limiting groove 401 needs to limit the shuttle in the vertical downward and downward directions to prevent it from deviating from the circular track, the upper limiting surface 402 and the lower limiting surface 403 are generally formed into conical surfaces, which is beneficial for limiting the shuttle during high-speed rotation. Therefore, there are certain requirements for the included angle between the upper limiting surface 402 and the lower limiting surface 403. Generally, the included angle α between the upper limiting surface 402 and the lower limiting surface 403 can be selected to be 60° to 160°, such as 80°, 90°, 100°, 120° or 140°, etc. This included angle refers to the angle formed by the generatrices of rotation of the upper limiting surface 402 and the lower limiting surface 403 on the same vertical plane. As shown in the figure, when the included angle of the limiting groove 401 is within the range of 60° to 160°, a stable surface contact area is formed between the limiting protrusion 11 and the limiting surface, and the contact area is dynamically adjusted with the change of angle. During shuttle operation, the vertical load is uniformly transmitted to the support roller 400 through surface contact, avoiding accelerated wear caused by localized stress concentration. At the same time, this angle range ensures that the opening width of the limiting groove 401 is within a reasonable range, which can accommodate the movement trajectory of the limiting protrusion 11 while limiting its vertical displacement, thereby suppressing the up-and-down floating of the shuttle.

[0034] To facilitate the assembly of the support roller 400, workers need to identify the direction during assembly. Therefore, in one embodiment, the upper limit surface 402 and the lower limit surface 403 are symmetrical about the horizontal plane, allowing normal use regardless of whether the upper limit surface 402 is on top or bottom. The upper limit surface 402 refers to the upper constraint surface in the concave limiting groove 401 on the outer peripheral side of the support roller 400, which contacts the limiting protrusion 11. Specifically, it can be implemented using an inclined plane or an arc surface, meaning the generatrix of rotation can be a straight line or an arc. Its function is to limit the upward displacement of the shuttle through contact with the limiting protrusion 11. Similarly, the lower limit surface 403 refers to the lower constraint surface in the concave limiting groove 401 on the outer peripheral side of the support roller 400, which contacts the limiting protrusion 11. Specifically, it can be implemented using an inclined plane or an arc surface symmetrical to the upper limit surface 402, meaning the generatrix of rotation can also be a straight line or an arc. Its function is to limit the downward displacement of the shuttle through contact with the limiting protrusion 11. In this context, horizontal symmetry refers to the mirror-symmetric distribution of the upper limit surface 402 and the lower limit surface 403 relative to the horizontal plane passing through the axis of the supporting roller 400. This can be achieved by designing the two limit surfaces with the same tilt angle and symmetrical arrangement. Their function is to provide symmetrical constraint forces in the vertical direction for the limit protrusion 11. Specifically, when the shuttleless shuttle 100 is running, the limit protrusion 11 is embedded in the limit groove 401, with its upper and lower surfaces contacting the upper limit surface 402 and the lower limit surface 403, respectively. Because the two limit surfaces are symmetrical about the horizontal plane, the constraint forces on the limit protrusion 11 in the vertical direction are symmetrically distributed, thus evenly suppressing the vertical displacement of the shuttle. When the shuttle is subjected to external forces and tends to move vertically, the symmetrical limit surfaces, through geometric constraints, convert the vertical offset into a tangential component force along the limit surfaces, thereby eliminating shuttle bounce. Compared with existing technologies, the upper and lower limiting surfaces 403 of the limiting groove 401 in traditional solutions typically employ an asymmetrical design or a single-plane constraint, resulting in an imbalance of the vertical constraint force on the shuttle and a tendency to float. This solution, through a symmetrical limiting surface structure, enables the constraint force to form a self-balancing mechanism in the vertical direction, significantly improving motion stability. Through the above technical solution, this application effectively suppresses vertical floating of the shuttle during operation, avoiding shuttle tilting or track deviation caused by excessive constraint force on one side, ensuring that the limiting protrusion 11 always moves along the central plane of the limiting groove 401, thereby eliminating shuttle jumping during weaving and ensuring fabric texture uniformity. In addition to the symmetrical design, considering the weight of the shuttle itself and the importance of the weft spindle, the lower limiting surface will bear a greater force. Therefore, in another embodiment, the angle of inclination of the lower limiting surface relative to the horizontal plane downwards can be designed to be smaller than the angle of inclination of the upper limiting surface relative to the horizontal plane upwards. This allows the lower limiting surface to better bear the weight and improve the stability of the shuttle's operation. Furthermore, to further improve the load-bearing capacity, the width of the lower limiting surface can be greater than the width of the upper limiting surface.

[0035] In one embodiment, the support roller 400 includes a mandrel 42 and an upper support sleeve 43, a limiting roller 44, and a lower support sleeve 45 sleeved on the mandrel 42. The upper support sleeve 43 abuts against the upper door ring 200 and the limiting roller 44, and the lower support sleeve 45 abuts against the lower door ring 300 and the limiting roller 44, thereby axially positioning the limiting roller 44. The mandrel 42 is a rigid rod-shaped component extending axially, which can be made of metal and is used to support the installation of the upper support sleeve 43, the limiting roller 44, and the lower support sleeve 45, and to provide basic support for axial positioning. The upper support sleeve 43 is an annular component sleeved on the top of the mandrel 42, which can be made of wear-resistant material and restricts the upward movement of the limiting roller 44 by abutting against the space between the upper door ring 200 and the limiting roller 44. The lower support sleeve 45 is an annular component fitted onto the bottom end of the mandrel 42. It can be made of the same material as the upper support sleeve 43 and restricts the downward movement of the limiting roller 44 by abutting against the space between the lower door ring 300 and the limiting roller 44. The limiting roller 44 is a cylindrical component fitted into the middle of the mandrel 42. It can be a bearing or a rigid sleeve structure and is used to contact the shuttle and provide rolling support. Its axial position is fixed by the bidirectional abutment of the upper support sleeve 43 and the lower support sleeve 45. Specifically, the mandrel 42, as the core component for axial positioning, passes through the upper door ring 200 and the lower door ring 300. The upper support sleeve 43 and the lower support sleeve 45 are respectively installed at both ends of the mandrel 42. During assembly, the upper support sleeve 43 is pressed between the top end of the mandrel 42 and the limiting roller 44, while the lower support sleeve 45 is pressed between the bottom end of the mandrel 42 and the limiting roller 44, forming a bidirectional clamping structure. This clamping method completely constrains the axial movement of the limiting roller 44, preventing roller position displacement caused by the gap 102 between the support sleeve and the limiting roller 44. Through the cooperation between the mandrel 42 and the support sleeve, the installation spacing of the limiting roller 44 is precisely controlled, thereby eliminating vertical floating and jumping of the shuttle caused by excessive spacing in the roller assembly. Compared with the prior art, in the prior art, two rollers are symmetrically installed on the support shaft with a fixed spacing, but the roller spacing cannot be dynamically adjusted according to assembly errors or wear, resulting in insufficient vertical stability of the shuttle. This solution, through the axial positioning structure of the mandrel 42 and the support sleeve, makes the installation position of the limiting roller 44 adjustable and gap-free 102, thereby reducing the roller spacing and maintaining rigid constraint, effectively suppressing vertical displacement during shuttle movement. Through the above technical solution, this application can precisely control the axial installation position of the limiting roller 44, eliminate the gap 102 caused by assembly errors or wear in the roller assembly, prevent vertical floating or jumping of the shuttle in circular motion, ensure the stability of the shuttle's running trajectory, and thus improve weaving quality.

[0036] The upper support sleeve 43 and the lower support sleeve 45 abut against the upper and lower ends of the limiting roller 44, respectively. To avoid affecting the rotation of the limiting roller 44, the limiting roller 44 can be designed to include an embedded upper bearing 441 and a lower bearing 442. The inner rings of both the upper bearing 441 and the lower bearing 442 are fitted to the spindle 42. The upper support sleeve 43 extends into the top of the limiting roller 44 and abuts against the inner ring of the upper bearing 441, while the lower support sleeve 45 extends into the bottom of the limiting roller 44 and abuts against the inner ring of the lower bearing 442. The upper bearing 441 and the lower bearing 442 are two rolling bearings installed inside the limiting roller 44. Specifically, deep groove ball bearings or angular contact bearings can be used to reduce the rotational frictional resistance between the limiting roller 44 and the spindle 42. The fit between the inner ring and the spindle 42 means that the inner ring of the bearing and the spindle 42 form an interference fit or a transition fit. Specifically, this can be achieved using a heat-fitting process or a press-fitting process, so that the inner ring of the bearing and the spindle 42 remain relatively stationary. The upper support sleeve 43 and the lower support sleeve 45 are annular parts fitted onto both ends of the mandrel 42. They can be made of metal and are used to apply axial pressure to the inner ring of the bearing. "Abutting against the inner ring" means that the end face of the support sleeve forms rigid contact with the end face of the inner ring of the bearing. This can be achieved through machining to ensure the flatness of the end faces, eliminating any gaps between the support sleeve and the inner ring. Specifically, after the inner ring of the bearing is fixed to the mandrel 42, the limiting roller 44 achieves rotational freedom through the outer ring of the bearing. The upper support sleeve 43 presses downward against the inner ring of the upper bearing 441, and the lower support sleeve 45 presses upward against the inner ring of the lower bearing 442, forming a bidirectional axial constraint. When the limiting roller 44 is subjected to axial force, the inner ring of the bearing is restricted from displacement by the support sleeve, preventing the bearing from shifting along the mandrel 42. The fixed fit between the mandrel 42 and the inner ring of the bearing ensures effective transmission of rotational torque, while the rigid contact between the support sleeve and the inner ring of the bearing forms an axial positioning reference. Compared to existing technologies, traditional structures rely solely on single-sided bearings or sliding sleeves for axial positioning of the rollers, resulting in accumulated clearance 102 and axial movement. This solution employs a double-sided bearing and bidirectional support sleeve structure, eliminating the axial assembly clearance 102. The rigid contact between the bearing inner ring and the support sleeve creates dual limiting, increasing axial positioning stiffness by approximately 40%. Through this technical solution, this application effectively suppresses the axial displacement of the limiting roller 44 on the mandrel 42, controlling the axial movement of the roller to within 0.05 mm, thus preventing vertical bouncing of the shuttle due to roller movement. The rigid contact between the bearing inner ring and the support sleeve provides stable axial constraint while maintaining the roller's rotational flexibility, reducing the shuttle's trajectory deviation to below 0.1 mm.

[0037] Although the support roller 400 has good wear resistance and a long service life, it is still a wear part compared to other circular loom products. Therefore, to facilitate the replacement of various components on the mandrel 42, the top of the mandrel 42 can be designed to extend upwards to form an upper retaining ring 200, and the bottom of the mandrel 42 can extend downwards to form a lower retaining ring 300. The two ends of the mandrel 42 are fixed by fasteners 421, which allow the upper retaining ring 200 and the lower retaining ring 300 to axially position the limiting roller 44. The mandrel 42 refers to the rigid support shaft that passes through the upper retaining ring 200, the lower retaining ring 300, and the limiting roller 44. It can be made of high-strength alloy steel and is used to transmit axial clamping force and form a symmetrical constraint path. The fasteners 421 are the connecting parts used to fix the two ends of the mandrel 42. They can be a combination of bolts and nuts, and the assembly gap 102 can be eliminated by adjusting the preload. The upper door ring 200 and lower door ring 300 refer to the upper and lower rigid frames that constitute the door ring assembly. A clamping force is applied by fasteners 421 at both ends of the mandrel 42, pressing the limiting roller 44 between them. Specifically, the top end of the mandrel 42 extends upward and passes through the upper door ring 200, and the bottom end extends downward and passes through the lower door ring 300. Both ends are locked and fixed by bolts and nuts. When the fasteners 421 are tightened, the upper door ring 200 and lower door ring 300 are subjected to opposing forces, generating an axial clamping force on the limiting roller 44. Since both ends of the mandrel 42 are rigidly fixed, the limiting roller 44 cannot move axially between the upper and lower door rings 300, thus eliminating displacement caused by the installation gap 102 or dynamic loads. The symmetrical extension design of the mandrel 42 ensures a uniform distribution of clamping force, avoiding eccentric deformation caused by unilateral fixing. By adjusting the preload of the fasteners 421, the assembly tolerance between the supporting roller 400 and the door ring can be further compensated, ensuring axial positioning accuracy. Compared with existing technologies, in traditional gate ring structures, the roller assembly achieves axial positioning only through single-sided fixing or partial snap-fitting, which is prone to gaps 102 due to vibration or wear, leading to changes in roller spacing. This solution, by extending the mandrel 42 symmetrically at both ends and applying bidirectional clamping force, forms a rigid axial constraint, effectively suppressing the movement of the support roller 400. Simultaneously, by adjusting the preload, it actively eliminates the assembly gap 102, significantly improving axial positioning reliability. Through the above technical solution, this application can avoid changes in roller spacing caused by axial displacement of the support roller 400 during operation, thereby preventing vertical floating and jumping of the shuttle, ensuring smooth shuttle operation along the circumferential track, and improving weaving quality stability. When replacing parts on the mandrel 42, the fastener 421 at the bottom of the mandrel 42 can be removed, and the mandrel 42 can be pulled upwards as a whole, or the fastener 421 at the top of the mandrel 42 can be removed, and the mandrel 42 can be pushed downwards as a whole, which is very convenient.

[0038] The wear-resistant flexible sleeve 41 includes an upper ring body 411 and a lower ring body 412. The recessed section 404 includes an upper conical surface 4041, a cylindrical surface 4042, and a lower conical surface 4043 from top to bottom. The upper ring body 411 is fixed to the upper conical surface 4041 and at least partially covers the cylindrical surface 4042 downwards. An upper limit surface 402 is provided on the upper ring body 411. The lower ring body 412 is fixed to the lower conical surface 4043 and at least partially covers the cylindrical surface 4042 upwards. A lower limit surface 403 is provided on the lower ring body 412. The upper ring body 411 refers to a split wear-resistant structure that covers the upper conical surface 4041 of the supporting roller 400 and extends to the top of the cylindrical surface 4042. Specifically, it can be fixed by using an injection molding process to bond rubber or polyurethane material to the upper conical surface 4041 and the cylindrical surface 4042. The axial constraint force generated by the inclination angle of the conical surface enhances the contact stability between the upper ring body 411 and the supporting roller 400. The lower ring 412 refers to a symmetrical split structure that covers the lower conical surface 4043 of the supporting roller 400 and extends to the bottom of the cylindrical surface 4042. Specifically, it can be fixed using the same material and process as the upper ring 411. The axial displacement of the lower ring 412 is limited by the tilt angle of the lower conical surface 4043, while forming a two-way wrapping of the cylindrical surface 4042 with the upper ring 411. The composite curved surface structure formed by the upper conical surface 4041, the cylindrical surface 4042, and the lower conical surface 4043 refers to the three-segment geometry of the recessed section 404 of the supporting roller 400. Specifically, it can be formed into a continuously transitioning curved surface by turning. The combination of the conical surface and the cylindrical surface 4042 is used to achieve precise positioning and stress dispersion of the wear-resistant flexible sleeve 41. Specifically, the upper ring 411 is fixed to the upper conical surface 4041 and extends downward to cover the top area of ​​the cylindrical surface 4042. The axial force generated by the inclination angle of the conical surface prevents the upper ring 411 from detaching upwards during shuttle operation. Simultaneously, covering the cylindrical surface 4042 increases the contact area to distribute vertical loads. The lower ring 412 is symmetrically fixed to the lower conical surface 4043 and extends upward to cover the bottom area of ​​the cylindrical surface 4042. The reverse axial force generated by the inclination angle of the lower conical surface 4043 constrains the lower ring 412 to move downwards. Together with the upper ring 411, they form a bidirectional covering of the cylindrical surface 4042, eliminating the risk of axial movement of the wear-resistant flexible sleeve 41 during high-speed friction. The upper limit surface 402 and the lower limit surface 403 are independently set on the upper ring 411 and lower ring 412, respectively. When a local area fails due to long-term wear, only the corresponding ring needs to be replaced to restore the limiting function, avoiding the need to replace the entire wear-resistant flexible sleeve 41. The composite curved surface structure allows the wear-resistant flexible sleeve 41 to decompose the impact force into axial and radial components through the conical angle when subjected to vertical impact, reducing stress concentration inside the material and improving structural durability. Compared with the existing technology, the traditional integral wear-resistant flexible sleeve 41 is directly sleeved on the cylindrical recessed section 404, relying solely on friction to resist axial displacement. During high-speed operation, stress concentration can easily lead to sleeve movement or localized wear.This solution utilizes a split ring body and a composite curved surface to enhance the sleeve's fixing effect through the axial constraint force generated by the conical surface. Simultaneously, the bidirectional coverage of the upper and lower ring bodies 412 on the cylindrical surface 4042 forms a mechanical limit, effectively suppressing axial displacement. Furthermore, the split structure allows for partial replacement of worn parts, significantly reducing maintenance costs compared to complete replacement. Through the above technical solution, this application solves the problems of axial displacement and localized wear caused by structural instability in the wear-resistant flexible sleeve 41. The synergistic effect of the split ring body and the composite curved surface ensures that the limiting groove 401 and the limiting protrusion 11 maintain a precise fit over a long period, extending the service life of the wear-resistant flexible sleeve 41 and maintaining the stability of the shuttle's running trajectory. The upper ring body 411 and the lower ring body 412 can also be an integral structure. To reduce the shearing effect of the limiting protrusion 11 on the wear-resistant flexible sleeve 41, the top of the limiting protrusion 11 can be designed with a rounded chamfer R1, improving the service life of the wear-resistant flexible sleeve 41. Since both the upper ring 411 and the lower ring 412 partially cover the cylindrical surface 4042, they can withstand the centrifugal force generated during the shuttle's movement. During the shuttle's circular motion, as it continuously contacts and leaves the support roller 400, it can effectively withstand the impact force, which not only improves the stability of the shuttle's movement but also reduces impact noise. It can also distribute the impact force borne by the upper limit surface 402 and the lower limit surface 403, thereby improving the overall lifespan of the wear-resistant flexible sleeve 41.

[0039] To ensure the service life of the wear-resistant flexible sleeve 41, the vertical thickness B1 of the upper ring 411 from the upper limit surface 402 to the upper conical surface 4041 can be controlled to be no less than 3mm, and the vertical thickness B2 of the lower ring 412 from the lower limit surface 403 to the lower conical surface 4043 can be controlled to be no less than 3mm. The upper ring 411 refers to the annular component covering the upper conical surface 4041 of the support roller 400 and extending downwards to the cylindrical surface 4042. Specifically, it can be made of vulcanized rubber or polyurethane material combined with a metal skeleton, increasing the vertical thickness to improve compressive strength. The lower ring 412 refers to the annular component covering the lower conical surface 4043 of the support roller 400 and extending upwards to the cylindrical surface 4042. Specifically, it can use the same materials and processes as the upper ring 411, ensuring rigid support through vertical thickness. Specifically, the vertical thickness of the upper ring 411 is set to be no less than 3mm, so that when the shuttle limiting protrusion 11 is pressed downward, the upper ring 411 can disperse the contact stress through sufficient material volume, avoiding the sinking of the limiting surface due to local deformation. The vertical thickness of the lower ring 412 is also no less than 3mm. When the shuttle is subjected to an upward force, the lower ring 412 maintains the positional stability of the lower limiting surface 403 through the structural stiffness formed by its thickness. At this thickness, the deformation of the flexible sleeve is controlled within the allowable range, thereby reducing the change in the vertical gap 102 caused by sleeve compression or wear. In some specific embodiments, the mating surface between the upper ring 411 and the upper conical surface 4041 can be designed as a stepped structure to increase the contact area, and an adhesive layer can be provided between the lower ring 412 and the lower conical surface 4043 to enhance the fixing effect. Compared with the prior art, the thickness of the ring of the flexible sleeve in the prior art is not clearly defined, which makes the material prone to creep or wear after long-term pressure, thus causing the shuttle to float vertically. This solution, by setting a minimum vertical thickness, ensures both the deformation resistance of the ring body itself and reduces the risk of stress concentration through optimized material volume distribution. Through this technical solution, this application effectively suppresses the vertical floating phenomenon of the shuttle during operation caused by insufficient thickness of the flexible sleeve, maintaining stable contact between the limiting protrusion 11 and the limiting groove 401, thereby ensuring the smooth movement of the shuttle along the circumferential track. Due to structural limitations, the bottom of the upper ring 411 gradually thins, and the top of the lower ring 412 gradually thins, correspondingly increasing elasticity to a certain extent and improving the shock absorption effect. Although the diameter of the support roller 400 should not be too large, since the cylindrical surface 4042 is the part with the smallest diameter of the limiting roller 44, to ensure the structural strength and service life of the support roller 400, the diameter D of the cylindrical surface 4042 can be required to be no less than 20mm. Because the limiting roller 44 has a shape that is thicker at both ends and thinner in the middle, considering the embedded devices of the upper bearing 441 and lower bearing 442, the cylindrical surface 4042 should not be too small either; otherwise, the upper limiting surface 402 and lower limiting surface 403 will be too inclined, which is not conducive to the movement and coordination of the limiting protrusion 11. The cylindrical surface 4042 refers to the outer circumferential surface of the support roller 400 that fits against the outer side of the shuttle. Specifically, it can be made by machining a cylindrical structure from metal material, and the radial support area can be increased by increasing the diameter of the cylindrical surface 4042. The requirement of a diameter of not less than 20mm means that the maximum straight-line distance of the cross-section of the cylindrical surface 4042 reaches or exceeds this value. This can be achieved by increasing the outer diameter of the mandrel 42 or adjusting the thickness of the wear-resistant flexible sleeve 41, ensuring that the roller assembly has sufficient bending stiffness and deformation resistance when bearing the load of the shuttle movement. Specifically, the setting of the diameter of the cylindrical surface 4042 directly affects the radial load-bearing capacity of the roller assembly. When the diameter increases, the contact area between the roller and the outer side of the shuttle increases accordingly, allowing the radial load to be evenly transmitted to the gate ring structure through a wider support surface. This design effectively disperses the local stress generated by the shuttle movement and avoids the expansion of the support gap 102 due to roller deformation. At the same time, the increased diameter of the cylindrical surface 4042 provides sufficient space for the machining of the limiting groove 401, allowing the contact area between the limiting protrusion 11 and the limiting groove 401 to maintain a stable matching relationship, thereby forming a more reliable constraint in the vertical direction. Compared to existing technologies, the diameter of the cylindrical 4042 surface of traditional roller assemblies is typically less than 20mm, resulting in insufficient radial support area. This makes them prone to elastic deformation during high-speed shuttle movement, exacerbating vertical float. This solution strengthens the structural rigidity of the roller assembly by limiting the lower limit of the cylindrical 4042 surface diameter, significantly suppressing the impact of roller spacing on shuttle float. Through this technical solution, this application enhances the radial support stability of the roller assembly, reduces vertical shuttle jump caused by excessive roller spacing, ensures the shuttle maintains a stable posture while running along the circumferential track, and thus improves the interlacing accuracy of warp and weft yarns during weaving.

[0040] This utility model also provides a shuttleless circular loom, including the shuttleless gate ring assembly described in any of the above embodiments, which greatly improves the stability of the shuttle movement, improves the weaving quality, and also helps to extend the service life of the support rollers, reduce the replacement frequency, and help ensure the working time of the circular loom and improve weaving efficiency.

[0041] In addition to the preferred embodiments described above, there are other embodiments of this utility model. All other embodiments obtained by those skilled in the art based on the embodiments of this utility model without creative effort are within the scope of protection claimed by this utility model.

Claims

1. A shuttleless gate ring assembly, comprising a shuttleless shuttle boat, an upper gate ring, a lower gate ring, and support rollers connecting the upper and lower gate rings, wherein multiple support rollers are distributed circumferentially along the gate ring assembly to form a circumferential track for the shuttleless shuttle boat to run on, characterized in that, The outer peripheral side of the support roller is provided with a concave limiting groove, which has an upper limiting surface and a lower limiting surface. The shuttle bottom plate of the shuttleless shuttle is provided with an outwardly protruding limiting protrusion. The limiting protrusion extends into the limiting groove and contacts and matches the upper limiting surface and the lower limiting surface respectively to achieve vertical limiting. There is a gap between the bottom surface of the shuttle bottom plate on both sides of the limiting protrusion and the outer peripheral side of the support roller.

2. The shuttleless door ring assembly according to claim 1, characterized in that, The outer periphery of the support roller is provided with a recessed section, and a wear-resistant flexible sleeve is fitted around the outer periphery of the recessed section. A limiting groove is provided on the outer periphery side of the wear-resistant flexible sleeve, and the limiting protrusion is a rigid protrusion that abuts against the outer periphery side of the wear-resistant flexible sleeve.

3. The shuttleless door ring assembly according to claim 1, characterized in that, The angle between the upper limit plane and the lower limit plane is 60° to 160°.

4. The shuttleless door ring assembly according to claim 1, characterized in that, The upper limit surface and the lower limit surface are symmetrical about the horizontal plane; and / or, the angle at which the lower limit surface is tilted downward relative to the horizontal plane is less than the angle at which the upper limit surface is tilted upward relative to the horizontal plane.

5. The shuttleless door ring assembly according to claim 1, characterized in that, The support roller includes a mandrel and an upper support sleeve, a limiting roller, and a lower support sleeve fitted on the mandrel. The upper support sleeve abuts between the upper door ring and the limiting roller, and the lower support sleeve abuts between the lower door ring and the limiting roller, thereby axially positioning the limiting roller.

6. The shuttleless door ring assembly according to claim 5, characterized in that, The limiting roller includes an embedded upper bearing and a lower bearing. The inner rings of the upper bearing and the lower bearing are both fitted with a spindle. The upper support sleeve extends into the top of the limiting roller and abuts against the inner ring of the upper bearing. The lower support sleeve extends into the bottom of the limiting roller and abuts against the inner ring of the lower bearing.

7. The shuttleless door ring assembly according to claim 5, characterized in that, The top end of the mandrel extends upward to form an upper door ring, and the bottom end of the mandrel extends downward to form a lower door ring. The two ends of the mandrel are fixed by fasteners so that the upper and lower door rings axially position the limiting roller.

8. The shuttleless door ring assembly according to claim 2, characterized in that, The wear-resistant flexible sleeve includes an upper ring body and a lower ring body. The recessed section includes an upper conical surface, a cylindrical surface and a lower conical surface from top to bottom. The upper ring body is fixed to the upper conical surface and at least covers part of the cylindrical surface downwards. An upper limit surface is provided on the upper ring body. The lower ring body is fixed to the lower conical surface and at least covers part of the cylindrical surface upwards. A lower limit surface is provided on the lower ring body.

9. The shuttleless door ring assembly according to claim 8, characterized in that, The vertical thickness of the upper ring body from the upper limit surface to the upper conical surface is not less than 3 mm, and the vertical thickness of the lower ring body from the lower limit surface to the lower conical surface is not less than 3 mm; and / or, the diameter of the cylindrical surface is not less than 20 mm.

10. A shuttleless circular loom, characterized in that, Includes the shuttleless door ring assembly as described in any one of claims 1 to 9.

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