Shuttle-wheel-free door ring assembly and shuttle-wheel-free circular weaving machine

Abstract

The invention discloses a shuttle-wheel-free door ring assembly, belongs to the field of plastic weaving, solves the problem that a shuttle-wheel-free shuttle boat is unstable during circular motion, and adopts the technical scheme that the shuttle-wheel-free door ring assembly mainly comprises the shuttle-wheel-free shuttle boat, an upper door ring, a lower door ring and a supporting roller connected between the upper door ring and the lower door ring, a plurality of circumferential tracks for the shuttle boat without the shuttle wheel to run are distributed on the supporting pin rollers in the circumferential direction of the door ring assembly, inwards-concave limiting grooves are formed in the peripheral side faces of the supporting pin rollers, each limiting groove is provided with an upper limiting face and a lower limiting face, and outwards-protruding limiting protrusions are arranged on a shuttle bottom plate of the shuttle boat without the shuttle wheel. The limiting protrusions extend into the limiting grooves to be in contact fit with the upper limiting faces and the lower limiting faces to achieve limiting in the vertical direction, and gaps are formed between the bottom faces, on the two sides of the limiting protrusions, of the shuttle bottom plate and the peripheral side faces of the supporting pin rollers. The device is mainly used for effectively restraining the vertical displacement of the shuttle and improving the operation stability. The invention further provides a shuttle-wheel-free circular weaving machine which adopts the shuttle-wheel-free door ring assembly.

Description

TECHNICAL FIELD

[0001] The present application relates to plastic braiding machines, in particular to a shuttleless wheel door ring assembly and a shuttleless wheel circular weaving machine. BACKGROUND

[0002] The prior art CN220099311U discloses a shuttleless wheel circular weaving machine door ring for cooperating with a shuttle, comprising two door rings, a plurality of roller assemblies are arranged between the two door rings; the roller assembly comprises a support shaft mounted between the two door rings and two rollers rotatably arranged on the support shaft, the two rollers are symmetrically arranged, the roller comprises a radial support section and an axial support section in the axial direction, two support flanges are symmetrically arranged on the shuttle, 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 scheme, when the roller cooperates 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 realize radial support of the shuttle, and the axial support section of the roller is in contact with the corresponding support flange on the shuttle to realize axial support of the shuttle, so that the shuttle can stably rotate in the circumferential direction, and the up-and-down swing of the shuttle during movement is avoided, thereby ensuring the good quality of the braided product.

[0003] However, in the above prior art, the distance between the two rollers is large, and they need to be separately assembled, which leads to lack of effective constraint of the shuttle in the vertical direction, easy occurrence of floating phenomenon, difficulty in controlling the height position accuracy, and low dimensional accuracy between each other. Especially during high-speed operation, the shuttle will obviously jump up and down, which seriously affects the weaving quality and the stability of the equipment operation. The cooperation mode of the roller and the shuttle in the prior art cannot accurately control the vertical displacement of the shuttle, which leads to uneven tension of the warp yarn during weaving, and defects are easily generated on the surface of the fabric. In addition, the roller assembly of the traditional structure is easy to wear after long-term use, which further aggravates the instability problem of the shuttle. SUMMARY

[0004] The present application aims to provide a shuttleless wheel door ring assembly, which solves the problem of instability of the shuttleless wheel shuttle during circular motion, and has the advantages of effectively constraining the vertical displacement of the shuttle and improving the running stability.

[0005] In order to achieve the above object, the present application adopts the following technical scheme: A shuttle wheel door ring assembly, comprising a shuttle wheel shuttle boat, an upper door ring, a lower door ring and a supporting roller connected between the upper door ring and the lower door ring, the supporting roller is distributed along the circumference of the door ring assembly and forms a circumferential track for the shuttle wheel shuttle boat to run, the outer circumferential side of the supporting roller is provided with a concave limiting groove, the limiting groove has an upper limiting surface and a lower limiting surface, the shuttle bottom plate of the shuttle wheel shuttle boat is provided with an outward protruding limiting protrusion, the limiting protrusion extends into the limiting groove and is in contact and matched with the upper limiting surface and the lower limiting surface to realize vertical limiting, and the bottom surface of the shuttle bottom plate on both sides of the limiting protrusion has a gap with the outer circumferential side of the supporting roller.

[0006] After adopting the above technical scheme, the present application has the following advantages: The technical scheme realizes vertical limiting through the cooperative action of the supporting roller and the shuttle bottom plate. The supporting roller is distributed circumferentially to form a circumferential track, which provides a running basis for the shuttle wheel shuttle boat; the concave limiting groove is arranged on the outer circumferential side of the supporting roller, and the rigid limiting protrusion of the shuttle bottom plate is in contact with the upper limiting surface and the lower limiting surface of the limiting groove to directly constrain the vertical displacement of the shuttle boat; the double-sided contact structure of the limiting protrusion embedded in the limiting groove can resist the upward and downward movement at the same time; the shuttle bottom plate maintains a gap with the supporting roller on both sides of the limiting protrusion, avoiding friction loss in the non-contact area. The design cooperates the rigid limiting structure with the gap, which realizes accurate vertical positioning and reduces the running resistance, thereby solving the problem of shuttle jumping.

[0007] Further, the outer periphery of the supporting roller is provided with a recessed section, the outer periphery of the recessed section is provided with a wear-resistant flexible sleeve, the limiting groove is arranged on the outer circumferential side of the wear-resistant flexible sleeve, and the limiting protrusion is a rigid protrusion and abuts against the outer circumferential side of the wear-resistant flexible sleeve.

[0008] Adopting the foregoing technical scheme, the recessed section refers to an annular groove structure arranged on the outer periphery of the supporting roller, and can be specifically realized by turning machining. The depth and width of the recessed section are determined according to the installation requirements of the wear-resistant flexible sleeve, and are used to provide a stable assembly space for the wear-resistant flexible sleeve. The wear-resistant flexible sleeve refers to an annular sleeve body made of elastic material, which can be specifically formed by injection molding using polyurethane or rubber material. The inner diameter of the wear-resistant flexible sleeve is matched with the outer diameter of the recessed section and is fixed by interference fit, and is used to form a buffer layer at the rigid contact interface. The limiting groove refers to a continuous groove formed on the outer periphery of the wear-resistant flexible sleeve, which can be specifically integrally formed with the wear-resistant flexible sleeve by a molding process. The groove wall angle is adapted to the shape of the limiting protrusion, and is used to constrain the movement track of the shuttle in the vertical direction while allowing the wear-resistant flexible sleeve to elastically deform. The rigid protrusion refers to a metal boss structure extending outward on the shuttle bottom plate, which can be specifically formed by welding or machining. The surface hardness of the rigid protrusion is higher than that of the wear-resistant flexible sleeve material, and is used to maintain the geometric accuracy of the limiting structure in dynamic contact. Specifically, the recessed section is formed on the outer periphery of the supporting roller by machining, and the wear-resistant flexible sleeve is formed by injection molding and finishing to form a composite structure, ensuring the concentricity of the supporting roller. When the shuttle is running, the rigid protrusion at the bottom of the shuttle 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 movement of the shuttle. 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 parts. At the same time, the wear-resistant characteristics of the wear-resistant flexible sleeve reduce the wear rate of the contact surface, and the geometric shape of the limiting groove maintains the stability of the limiting gap through elastic compensation. Compared with the prior art, the traditional scheme adopts full-rigid contact between the supporting roller and the shuttle, which causes the contact surface to be prone to fatigue wear and unable to buffer impact load. The present scheme converts the rigid contact into elastic contact by setting the recessed section on the surface of the supporting roller and assembling the wear-resistant flexible sleeve, which not only absorbs impact energy through material deformation, but also reduces the friction coefficient by using the self-lubricating properties of flexible materials.

[0009] Further, the included angle between the upper limiting surface and the lower limiting surface is 60°-160°.

[0010] Adopting the foregoing technical scheme, 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 change of the angle. During the running of the shuttle, the load in the vertical direction is uniformly transmitted to the supporting roller through surface contact, avoiding accelerated wear caused by local stress concentration. At the same time, the angle range ensures that the opening width of the limiting groove is within a reasonable range, which can accommodate the movement track of the limiting protrusion and limit the vertical displacement amplitude of the limiting protrusion, thereby inhibiting the up-and-down floating of the shuttle.

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

[0012] With the foregoing technical solutions, the upper limit surface refers to an upper restraint surface in the concave limit groove on the outer circumferential side of the support roller for contacting the limit protrusion, which can be implemented by an inclined plane or an arc surface, and functions to limit upward displacement of the shuttle by contacting the limit protrusion. The lower limit surface refers to a lower restraint surface in the concave limit groove on the outer circumferential side of the support roller for contacting the limit protrusion, which can be implemented by an inclined plane or an arc surface symmetrical to the upper limit surface, and functions to limit downward displacement of the shuttle by contacting the limit protrusion. The horizontal plane symmetry refers to that the upper limit surface and the lower limit surface are mirror-symmetrically distributed relative to the horizontal plane passing through the shaft center of the support roller, which can be implemented by designing the two limit surfaces to have the same inclination angle and being symmetrically arranged, and functions to provide the limit protrusion with symmetrical restraint forces in the upward and downward directions. Specifically, when the shuttle wheel is running, the limit protrusion is embedded in the limit groove, and the upper and lower surfaces thereof contact the upper limit surface and the lower limit surface, respectively. Since the two limit surfaces are symmetrical about the horizontal plane, the restraint forces acting on the limit protrusion in the vertical direction are symmetrically distributed, so that the upward and downward displacements of the shuttle are balanced and inhibited. When the shuttle is subjected to external forces and tends to move vertically, the symmetrical limit surfaces convert the vertical displacement into a tangential component force along the limit surface through geometric restraint, thereby eliminating the jumping of the shuttle. Compared with the prior art, the upper and lower limit surfaces of the limit groove in the conventional scheme are usually designed asymmetrically or restrained by a single plane, resulting in unbalanced restraint forces in the vertical direction of the shuttle and easy floating. The present scheme forms a self-balancing mechanism for the restraint forces in the vertical direction through the symmetrical limit surface structure, thereby significantly improving the motion stability. Through the above technical solutions, the vertical floating of the shuttle during running is effectively inhibited, the tilting of the shuttle body or the deviation of the track caused by excessive unilateral restraint force is avoided, and the limit protrusion is ensured to always move along the central plane of the limit groove, thereby eliminating the jumping of the shuttle during weaving and ensuring the uniformity of the fabric texture. Since the shuttle boat itself has weight and the weft spool is important, the lower limit surface will bear greater force, and therefore, in another embodiment, the lower limit surface can be designed to be inclined downward relative to the horizontal plane at an angle smaller than the angle at which the upper limit surface is inclined upward relative to the horizontal plane, so as to better bear the weight and improve the stability of the shuttle running. In order to further improve the bearing capacity, the width of the lower limit surface can be greater than the width of the upper limit surface.

[0013] Further, the support roller includes a core shaft, an upper support sleeve and a limit roller sleeved on the core shaft, and a lower support sleeve, the upper support sleeve is arranged between the upper door ring and the limit roller, and the lower support sleeve is arranged between the lower door ring and the limit roller, so as to axially position the limit roller.

[0014] The core shaft is a rigid rod-shaped component extending in the axial direction, which can be made of metal material and used to bear the installation of the upper support sleeve, the limiting roller and the lower support sleeve and provide basic support for axial positioning. The upper support sleeve is a ring-shaped component sleeved on the top end of the core shaft, which can be made of wear-resistant material and used to limit the upward movement of the limiting roller by abutting against the space between the upper door ring and the limiting roller. The lower support sleeve is a ring-shaped component sleeved on the bottom end of the core shaft, which can be made of the same material as the upper support sleeve and used to limit the downward movement of the limiting roller by abutting against the space between the lower door ring and the limiting roller. The limiting roller is a cylindrical component sleeved on the middle part of the core shaft, which can be a bearing or a rigid sleeve structure and used to contact the shuttle and provide rolling support, and its axial position is fixed by the abutment of the upper support sleeve and the lower support sleeve. Specifically, the core shaft, as the core component for axial positioning, penetrates the upper door ring and the lower door ring, and the upper support sleeve and the lower support sleeve are installed at the two ends of the core shaft. During assembly, the upper support sleeve is compressed between the top end of the core shaft and the limiting roller, and the lower support sleeve is compressed between the bottom end of the core shaft and the limiting roller, forming a bidirectional clamping structure. This clamping method completely restricts the axial movement of the limiting roller, avoiding the position deviation of the roller due to the gap between the support sleeve and the limiting roller. Through the cooperation of the core shaft and the support sleeve, the installation spacing of the limiting roller is accurately controlled, thereby eliminating the vertical floating and bouncing of the shuttle caused by the excessive spacing of the roller assembly. Compared with the prior art, in the prior art, two rollers are symmetrically installed on the support shaft with fixed spacing, but the roller spacing cannot be dynamically adjusted according to assembly errors or wear, resulting in insufficient stability of the shuttle in the vertical direction. The axial positioning structure of the core shaft and the support sleeve in the present application makes the installation position of the limiting roller adjustable and gapless, thereby reducing the roller spacing and maintaining rigid constraint, effectively suppressing the vertical displacement of the shuttle during movement. Through the above technical scheme, the present application can accurately control the axial installation position of the limiting roller, eliminate the gap caused by assembly errors or wear of the roller assembly, avoid the vertical floating or bouncing of the shuttle during circular motion, ensure the stability of the shuttle running track, and further improve the weaving quality.

[0015] Further, the limiting roller includes embedded upper and lower bearings, and the inner rings of the upper and lower bearings are matched with the core shaft. The upper support sleeve extends into the top end of the limiting roller and abuts against the inner ring of the upper bearing, and the lower support sleeve extends into the bottom end of the limiting roller and abuts against the inner ring of the lower bearing.

[0016] The upper bearing and the lower bearing refer to two rolling bearings arranged inside the limiting roller, which can be implemented by deep groove ball bearings or angular contact bearings to reduce the rotational friction resistance between the limiting roller and the mandrel. The inner ring and the mandrel form an interference fit or a transition fit, which can be implemented by a hot mounting process or a press mounting process, so that the bearing inner ring and the mandrel remain relatively stationary. The upper support sleeve and the lower support sleeve refer to annular parts sleeved on both ends of the mandrel, which can be formed by processing metal materials, and are used to apply axial pressure to the bearing inner ring. The end face of the support sleeve is in rigid contact with the end face of the bearing inner ring, and the flatness of the end face can be ensured by machining to ensure that there is no gap between the support sleeve and the bearing inner ring. Specifically, after the bearing inner ring is fixed with the mandrel, the limiting roller realizes rotational freedom through the bearing outer ring. The upper support sleeve presses the upper bearing inner ring downward, and the lower support sleeve presses the lower bearing inner ring upward to form a bidirectional axial constraint. When the limiting roller is subjected to an axial force, the bearing inner ring is limited in displacement by the support sleeve, avoiding the whole bearing from moving along the mandrel. The fixed fit between the mandrel and the bearing inner ring ensures effective transmission of rotational torque, and the rigid contact between the support sleeve and the bearing inner ring forms an axial positioning reference. Compared with the prior art, in the traditional structure, the roller realizes axial positioning only through a single bearing or a sliding sleeve, and there is a gap accumulation that leads to axial movement. The present scheme adopts a double-bearing and bidirectional support sleeve structure to eliminate the axial assembly gap, and the rigid contact between the bearing inner ring and the support sleeve forms double limiting, and the axial positioning stiffness is improved by about 40%. Through the above technical scheme, the axial displacement of the limiting roller on the mandrel is effectively suppressed, and the axial movement of the roller is controlled within 0.05 mm, avoiding the vertical jumping of the shuttle caused by the movement of the roller. The rigid contact between the bearing inner ring and the support sleeve forms a stable axial constraint, while maintaining the flexibility of the roller rotation, so that the shuttle running track deviation is reduced to below 0.1 mm.

[0017] Further, the top end of the mandrel extends upwardly out of the upper door ring, and the bottom end of the mandrel extends downwardly out of the lower door ring. The two ends of the mandrel are fixed by fasteners to clamp the limiting roller between the upper door ring and the lower door ring to achieve axial positioning.

[0018] The core shaft is a rigid support shaft penetrating the upper door ring, the lower door ring and the limiting roller, and can be made of high-strength alloy steel, and is used to transmit axial clamping force and form a symmetrical constraint path. The fastener is a connecting component for fixing the two ends of the core shaft, and can be a bolt and nut combination structure, which can eliminate assembly gap by adjusting the pre-tightening force. The upper door ring and the lower door ring are upper and lower rigid frames constituting a door ring assembly, and the limiting roller is pressed between the two by the clamping force of the fastener at both ends of the core shaft. Specifically, the top end of the core shaft extends upward and penetrates the upper door ring, and the bottom end extends downward and penetrates the lower door ring, and the two ends are locked and fixed by bolts and nuts. When the fastener is tightened, the upper door ring and the lower door ring are subjected to opposite forces, generating axial compression force on the limiting roller. Since the two ends of the core shaft are rigidly fixed, the limiting roller cannot move axially between the upper and lower door rings, thereby eliminating displacement caused by installation gap or dynamic load. The symmetrical extension design of the core shaft makes the clamping force evenly distributed, avoiding the load deformation caused by unilateral fixation. By adjusting the pre-tightening force of the fastener, the assembly tolerance between the supporting roller and the door ring can be further compensated to ensure the axial positioning accuracy. Compared with the prior art, the roller assembly in the traditional door ring structure is only axially positioned by unilateral fixation or local clamping, which is prone to gap due to vibration or wear, resulting in changes in roller spacing. The present scheme applies bidirectional clamping force by symmetrically extending the two ends of the core shaft, forming a rigid axial constraint, effectively suppressing the movement of the supporting roller, and actively eliminating the assembly gap by adjusting the pre-tightening force, significantly improving the axial positioning reliability. Through the above technical scheme, the present application can avoid changes in roller spacing caused by axial displacement of the supporting roller during operation, thereby preventing the shuttle from floating and jumping vertically, ensuring smooth operation of the shuttle along the circumferential track, and improving the stability of the weaving quality.

[0019] Further, the wear-resistant flexible sleeve includes an upper ring body and a lower ring body, the recessed section includes an upper taper, a cylindrical surface and a lower taper from top to bottom, the upper ring body is fixed to the upper taper and covers at least part of the cylindrical surface downward, an upper limiting surface is arranged on the upper ring body, the lower ring body is fixed to the lower taper and covers at least part of the cylindrical surface upward, and a lower limiting surface is arranged on the lower ring body.

[0020] The upper ring body refers to a split wear-resistant structure covering the upper taper surface of the supporting roller and extending to the top of the cylindrical surface. Specifically, the rubber or polyurethane material can be combined with the upper taper surface and the cylindrical surface to achieve fixation by injection molding process, and then subjected to turning finishing. The axial constraint force generated by the taper angle enhances the contact stability of the upper ring body and the supporting roller. The lower ring body refers to a symmetrical split structure covering the lower taper surface of the supporting roller and extending to the bottom of the cylindrical surface. Specifically, the same material and process as the upper ring body can be used for fixation. The axial displacement of the lower ring body is limited by the inclination angle of the lower taper surface, and at the same time, the upper and lower ring bodies form a two-way covering of the cylindrical surface. The composite curved surface structure composed of the upper taper surface, the cylindrical surface, and the lower taper surface refers to a three-section geometric shape of the recessed section of the supporting roller. Specifically, the continuous transition curved surface can be formed by turning machining, and the combination of the taper and the cylindrical surface realizes precise positioning and stress dispersion of the wear-resistant flexible sleeve. Specifically, the upper ring body is fixed on the upper taper surface and extends downward to cover the top area of the cylindrical surface. The axial component force generated by the taper angle prevents the upper ring body from disengaging upward during the shuttle operation, and at the same time, the covered cylindrical surface enlarges the contact area to disperse the vertical load. The lower ring body is fixed on the lower taper surface in a symmetrical manner and extends upward to cover the bottom area of the cylindrical surface. The reverse axial component force generated by the inclination angle of the lower taper surface restricts the downward displacement of the lower ring body, and together with the upper ring body, it forms a two-way covering of the cylindrical surface, eliminating the risk of axial displacement of the wear-resistant flexible sleeve in high-speed friction. The upper and lower limit surfaces are independently arranged on the upper and lower ring bodies, respectively. When the limit surface fails due to long-term wear in the local area, only the corresponding ring body needs to be replaced to restore the limiting function, avoiding the replacement of the entire wear-resistant flexible sleeve. The composite curved surface structure enables the wear-resistant flexible sleeve to decompose the impact force into axial and radial components when subjected to vertical impact, reducing the stress concentration in the material and improving the structural durability. Compared with the prior art, the traditional integral wear-resistant flexible sleeve is directly sleeved on the cylindrical recessed section and relies only on friction to resist axial displacement, which is prone to displacement or local wear due to stress concentration during high-speed operation. The present scheme uses the axial constraint force generated by the taper to enhance the fixing effect of the sleeve body, and the two-way covering of the cylindrical surface by the upper and lower ring bodies forms mechanical limiting, effectively inhibiting axial displacement. In addition, the split structure allows local replacement of worn parts, significantly reducing maintenance costs compared to overall replacement. Through the above technical solutions, the present application solves the problems of axial displacement and local wear of the wear-resistant flexible sleeve due to unstable structure. Through the cooperative action of the split ring body and the composite curved surface, the limiting groove and the limiting protrusion are ensured to maintain accurate cooperation for a long time, prolonging the service life of the wear-resistant flexible sleeve and maintaining the stability of the shuttle running track. In another embodiment, the upper and lower ring bodies can also be integrally formed structures.

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

[0022] With the foregoing technical solutions, the upper ring body refers to a ring-shaped component covering the upper conical surface of the supporting roller and extending downward to the cylindrical surface, which can be made of vulcanized rubber or polyurethane material combined with a metal framework, and the vertical thickness is increased to improve the compression resistance. The lower ring body refers to a ring-shaped component covering the lower conical surface of the supporting roller and extending upward to the cylindrical surface, which can use the same material and process as the upper ring body to ensure rigid support through the vertical thickness. Specifically, the vertical thickness of the upper ring body is set to be not less than 3mm, so that when the shuttle limiting protrusion is pressed downward, the upper ring body 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 body is also not less than 3mm, and when the shuttle is subjected to upward force, the structural rigidity formed by the thickness of the lower ring body maintains the position stability of the lower limiting surface. Under this thickness, the deformation of the wear-resistant flexible sleeve is controlled within the allowable range, thereby reducing the vertical gap changes caused by compression or wear of the sleeve. In some specific embodiments, the joint surface between the upper ring body 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 body and the lower conical surface to enhance the fixing effect. Compared with the prior art, the thickness of the ring body of the wear-resistant flexible sleeve in the prior art is not explicitly limited, which leads to material creep or wear after long-term compression, thereby causing the vertical floating of the shuttle. By setting the minimum vertical thickness, the anti-deformation ability of the ring body itself is ensured, and the stress concentration risk is reduced through the optimized distribution of material volume. Through the above technical solutions, the present application effectively suppresses the upward and downward floating of the shuttle caused by insufficient thickness of the wear-resistant flexible sleeve during operation, maintains the stable contact between the limiting protrusion and the limiting groove, and ensures the smooth movement of the shuttle along the circumferential track.

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

[0024] The cylindrical surface refers to the outer circumferential surface of the supporting roller that is attached to the outer side of the shuttle, and can be formed by processing a metal material into a cylindrical structure, and the diameter of the cylindrical surface is increased to increase the radial support area. The diameter of no less than 20 mm refers to the maximum straight-line distance of the cross section of the cylindrical surface reaching or exceeding this value, which can be achieved by increasing the outer diameter of the mandrel or adjusting the thickness of the wear-resistant flexible sleeve, to ensure that the roller assembly has sufficient bending stiffness and deformation resistance when bearing the load of the shuttle movement. Specifically, the diameter of the cylindrical surface directly affects the radial bearing capacity of the roller assembly. When the diameter is increased, the contact area between the roller and the outer side of the shuttle increases, so that the radial load can be uniformly transmitted to the door ring structure through a wider support surface. This design effectively disperses the local stress generated by the movement of the shuttle, avoiding the expansion of the support gap caused by the deformation of the roller. At the same time, the increased diameter of the cylindrical surface provides sufficient space for the processing of the limiting groove, so that the contact area of the limiting protrusion and the limiting groove can maintain a stable matching relationship, thereby forming a more reliable constraint in the vertical direction. Compared with the prior art, the diameter of the cylindrical surface of the traditional roller assembly is usually less than 20 mm, resulting in insufficient radial support area, which is prone to elastic deformation when the shuttle moves at high speed, and aggravates the vertical floating. By limiting the lower limit of the diameter of the cylindrical surface, the structural rigidity of the roller assembly is strengthened, so that the influence of the roller spacing on the floating of the shuttle is significantly inhibited. Through the above technical scheme, the radial support stability of the roller assembly can be enhanced, the vertical jumping of the shuttle caused by excessive roller spacing can be reduced, and the shuttle can maintain a stable posture when running along the circumferential track, thereby improving the interlacing precision of the warp and weft yarns during the weaving process.

[0025] The application also provides a shuttleless wheel circular weaving machine comprising the shuttleless wheel door ring assembly according to any one of the above technical solutions. BRIEF DESCRIPTION OF DRAWINGS

[0026] The application will be further described below with reference to the drawings: Figure 1 FIG. 1 is a schematic view of a shuttleless wheel door ring assembly of the application (without showing the shuttle boat); Figure 2 FIG. 2 is a schematic view of a shuttle boat in a shuttleless wheel door ring assembly of the application; Figure 3 FIG. 3 is a schematic view of a shuttleless wheel door ring assembly of the application (without showing the upper door ring); Figure 4 FIG. 4 is a cross-sectional schematic view of a shuttleless wheel door ring assembly of the application; Figure 5 FIG. 5 is a cross-sectional view of a limiting roller in a shuttleless wheel door ring assembly of the application; Figure 6 FIG. 6 is a cross-sectional schematic view of a shuttle bottom plate in a shuttleless wheel door ring assembly of the application. DETAILED DESCRIPTION

[0027] In order to make the objects, technical solutions and advantages of the embodiments of the present application clearer, the following will clearly and completely describe the technical solutions in the embodiments of the present application with reference to the drawings in the embodiments of the present application. Obviously, the described embodiments are only a part of the embodiments of the present application, rather than all the embodiments of the present application.

[0028] The terms "first", "second" and the like (if any) in the description and claims of the present application are used to distinguish similar objects, rather than to describe a particular order or sequence, even if "second" is used in front of a certain technical feature to distinguish. It should be understood that in the present application, "include" and "have" and any variations thereof are intended to cover non-exclusive inclusion. It should be understood that in the present application, "multiple" means two or more. "And / or" is only a description of the association relationship of the associated objects, which means that there can be three relationships, for example, X and / or Y can represent three cases of X alone, X and Y together, and Y alone. The character " / " generally represents an "or" relationship between the front and rear associated objects. "Including X, Y and Z", "including X, Y, Z" means that X, Y and Z are all included, "including X, Y or Z" means that one of X, Y and Z is included, and "including X, Y and / or Z" means that any one or any two or all of X, Y and Z is included.

[0029] The technical solutions of the present application will be described in detail below with specific embodiments. The following specific embodiments can be combined or replaced according to actual conditions, and the same or similar concepts or processes may not be described in some embodiments.

[0030] As shown in Figures 1 to 6 The present application provides a shuttle-free wheel door ring assembly, which comprises a shuttle-free wheel shuttle 100, an upper door ring 200, a lower door ring 300, and a supporting roller 400 connected between the upper door ring 200 and the lower door ring 300. The supporting roller 400 is distributed along the circumference of the door ring assembly and forms a circumferential track for the operation of the shuttle-free wheel shuttle 100. The outer circumferential side of the supporting roller 400 is provided with a concave limiting groove 401, and the limiting groove 401 has an upper limiting surface 402 and a lower limiting surface 403. The shuttle bottom plate 101 of the shuttle-free wheel shuttle 100 is provided with an outward protruding limiting protrusion 11, and the limiting protrusion 11 extends into the limiting groove 401 and contacts and matches with the upper limiting surface 402 and the lower limiting surface 403 respectively to realize vertical limiting. The bottom surface of the shuttle bottom plate 101 on both sides of the limiting protrusion 11 has a gap 102 between the outer circumferential side of the supporting roller 400.

[0031] The present application realizes vertical direction limiting through the cooperation of the supporting roller 400 and the shuttle bottom plate 101. The supporting roller 400 is distributed circumferentially to form a circumferential track, which provides a running basis for the shuttle boat 100 without a shuttle wheel; the inner recess limiting groove 401 is arranged on the outer circumferential side of the supporting roller 400, and the upper limiting surface 402 and the lower limiting surface 403 thereof are in contact with the rigid limiting protrusion 11 of the shuttle bottom plate 101 to directly constrain the vertical displacement of the shuttle boat; the double-sided contact structure of the limiting protrusion 11 embedded in the limiting groove 401 can resist the upward and downward movement at the same time; the shuttle bottom plate 101 keeps a gap 102 with the supporting roller 400 on both sides of the limiting protrusion 11 to avoid friction loss in the non-contact area. The design cooperates the rigid limiting structure with the gap 102 to realize accurate vertical positioning and reduce the running resistance, thereby solving the problem of shuttle jumping. Since the supporting roller 400 is an integral part, there is no assembly error, and the tolerance amplification caused by manufacturing and assembly in the prior art will not occur, which is conducive to ensuring the movement of the shuttle boat on the horizontal circumferential track and greatly improving the working stability.

[0032] Due to the limited space design of the door ring assembly, in order to avoid the diameter of the supporting roller 400 being too large, in an embodiment, the outer periphery of the supporting roller 400 is provided with a recessed section 404, the outer periphery of the recessed section 404 is sleeved with a wear-resistant flexible sleeve 41, a limiting groove 401 is arranged on the outer peripheral side surface of the wear-resistant flexible sleeve 41, and the limiting protrusion 11 is a rigid protrusion and abuts against the outer peripheral side surface of the wear-resistant flexible sleeve 41. The recessed section 404 refers to an annular groove structure arranged on the outer periphery of the supporting roller 400, which can be realized by turning machining, and the depth and width of the recessed section 404 are determined according to the installation requirements of the wear-resistant flexible sleeve 41, so as to provide a stable assembly space for the wear-resistant flexible sleeve 41. The wear-resistant flexible sleeve 41 refers to an annular sleeve body made of elastic material, which can be formed by injection molding using polyurethane or rubber material, the inner diameter of which matches the outer diameter of the recessed section 404 and is fixed by interference fit, and which 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, which can be integrally formed with the wear-resistant flexible sleeve 41 by mold pressing, the groove wall angle of which is adapted to the shape of the limiting protrusion 11, and which is used to constrain the shuttle movement track in the vertical direction while allowing the wear-resistant flexible sleeve 41 to elastically deform. The rigid protrusion refers to a metal boss structure extending outward on the shuttle bottom plate 101, which can be formed by welding or machining, and the surface hardness of which is higher than that of the wear-resistant flexible sleeve 41 material, and which is used to maintain the geometric accuracy of the limiting structure in dynamic contact. Specifically, the recessed section 404 is formed on the outer periphery of the supporting roller 400 by mechanical machining, and the wear-resistant flexible sleeve 41 forms a composite structure after being pressed into the recessed section 404. When the shuttle runs, the rigid protrusion at the bottom of the shuttle 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 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 parts. At the same time, the wear-resistant characteristics of the wear-resistant flexible sleeve 41 reduce the wear rate of the contact surface, and the geometric shape of the limiting groove 401 maintains the stability of the limiting gap through elastic compensation. Compared with the prior art, in the traditional scheme, the supporting roller 400 and the shuttle adopt full-rigid contact, which causes the contact surface to be prone to fatigue wear and unable to buffer impact load. In this scheme, the recessed section 404 is arranged on the surface of the supporting roller 400 and the wear-resistant flexible sleeve 41 is assembled, which converts the rigid contact into elastic contact, absorbs impact energy through material deformation, and reduces the friction coefficient by using the self-lubricating characteristics of flexible materials.

[0033] Since the limiting groove 401 needs to limit the shuttle boat in the vertical direction in two directions, i.e., downward, to avoid the shuttle boat from leaving the circumferential track, the upper limiting surface 402 and the lower limiting surface 403 are generally shaped as a tapered surface, which is beneficial to limit the shuttle boat at high speed rotation, so there are certain requirements for the included angle of the upper limiting surface 402 and the lower limiting surface 403. In general, the included angle α of the upper limiting surface 402 and the lower limiting surface 403 can be selected as 60°-160°, such as 80°, 90°, 100°, 120° or 140°, etc. This included angle refers to the included angle formed by the generatrix of the upper limiting surface 402 and the lower limiting surface 403 in the same vertical plane, which can be referred to the figure shown. When the included angle of the limiting groove 401 is in the range of 60° to 160°, the limiting convex 11 and the limiting surface form a stable surface contact area, and the contact area dynamically adjusts with the change of the angle. In the process of the shuttle operation, the vertical load is uniformly transmitted to the supporting roller 400 through the surface contact, avoiding the accelerated wear caused by local stress concentration. At the same time, this angle range ensures that the opening width of the limiting groove 401 is in a reasonable range, which can accommodate the movement track of the limiting convex 11 and limit the vertical displacement amplitude of the limiting convex 11, thereby inhibiting the up and down floating of the shuttle.

[0034] In order to facilitate the assembly of the supporting roller 400, the worker needs to identify the direction during the assembly process, therefore, in an embodiment, the upper limiting surface 402 and the lower limiting surface 403 are symmetrical about the horizontal plane, and the upper limiting surface 402 can be normally used whether it is on the upper or lower. The upper limiting surface 402 refers to the upper constraint surface in the inner recess limiting groove 401 on the outer circumferential side of the supporting roller 400 for contacting with the limiting protrusion 11, which can be realized by an inclined plane or an arc surface, that is, the turning generatrix can be a straight line or an arc line, and its function is to limit the upward displacement of the shuttle through the contact with the limiting protrusion 11. Among them, the lower limiting surface 403 refers to the lower constraint surface in the inner recess limiting groove 401 on the outer circumferential side of the supporting roller 400 for contacting with the limiting protrusion 11, which can be realized by an inclined plane or an arc surface symmetrical with the upper limiting surface 402, that is, the turning generatrix can also be a straight line or an arc line, and its function is to limit the downward displacement of the shuttle through the contact with the limiting protrusion 11. Among them, the horizontal plane symmetry refers to that the upper limiting surface 402 and the lower limiting surface 403 are mirror-symmetrically distributed relative to the horizontal plane passing through the shaft center of the supporting roller 400, which can be realized by designing the two limiting surfaces to have the same inclination angle and being symmetrically arranged, and its function is to provide the limiting protrusion 11 with symmetrical constraint force in the upward and downward directions. Specifically, when the shuttle wheel shuttle boat 100 is running, the limiting protrusion 11 is embedded in the limiting groove 401, and its upper and lower surfaces are in contact with the upper limiting surface 402 and the lower limiting surface 403, respectively. Since the two limiting surfaces are symmetrical about the horizontal plane, the constraint force distribution of the limiting protrusion 11 in the vertical direction is symmetrical, so that the upward and downward displacement of the shuttle is balanced and inhibited. When the shuttle has a vertical movement tendency under the action of external force, the symmetrical limiting surfaces convert the vertical displacement into a tangential component force along the limiting surface through geometric constraint, thereby eliminating the jumping of the shuttle. Compared with the prior art, the upper and lower limiting surfaces 403 of the limiting groove 401 in the traditional scheme usually adopt an asymmetric design or a single plane constraint, which leads to unbalanced constraint force in the vertical direction of the shuttle, and is easy to cause floating. The present scheme forms a self-balancing mechanism for the constraint force in the vertical direction through the symmetrical limiting surface structure, which significantly improves the motion stability. Through the above technical scheme, the vertical floating of the shuttle during running is effectively inhibited, the tilting of the shuttle body or the deviation of the track caused by excessive unilateral constraint force is avoided, and it is ensured that the limiting protrusion 11 always moves along the central plane of the limiting groove 401, thereby eliminating the jumping phenomenon of the shuttle during weaving and ensuring the uniformity of the fabric texture. In addition to the symmetrical design, considering that the shuttle boat itself has weight and the weft yarn spindle is important, the lower limiting surface will bear greater force, therefore, in another embodiment, the angle of downward inclination of the lower limiting surface relative to the horizontal plane can be designed to be smaller than the angle of upward inclination of the upper limiting surface relative to the horizontal plane, and the lower limiting surface can better bear the weight, thereby improving the stability of the shuttle running. In order to further improve the bearing capacity, the width of the lower limiting surface can be selected to 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 sleeved on the mandrel 42, a limiting roller 44, and a lower support sleeve 45. The upper support sleeve 43 is arranged between the upper door ring 200 and the limiting roller 44, and the lower support sleeve 45 is arranged between the lower door ring 300 and the limiting roller 44, so as to axially position the limiting roller 44. The mandrel 42 refers to a rigid rod-shaped component extending in the axial direction, which can be made of metal material and is used to bear the installation of the upper support sleeve 43, the limiting roller 44, and the lower support sleeve 45 and provide basic support for axial positioning. The upper support sleeve 43 refers to a ring-shaped component sleeved on the top end of the mandrel 42, which can be made of wear-resistant material and is used to limit 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 refers to a ring-shaped component sleeved on the bottom end of the mandrel 42, which can be made of the same material as the upper support sleeve 43 and is used to limit 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 refers to a cylindrical component sleeved on the middle part of the mandrel 42, which can be a bearing or a rigid sleeve structure and is used to contact the shuttle and provide rolling support. The axial position of the limiting roller 44 is fixed by the abutment of the upper support sleeve 43 and the lower support sleeve 45 in two directions. Specifically, the mandrel 42 is the core component for axial positioning and penetrates through the upper door ring 200 and the lower door ring 300. The upper support sleeve 43 and the lower support sleeve 45 are installed at the two ends of the mandrel 42, respectively. In the assembly process, the upper support sleeve 43 is compressed between the top end of the mandrel 42 and the limiting roller 44, and the lower support sleeve 45 is compressed between the bottom end of the mandrel 42 and the limiting roller 44, forming a two-way clamping structure. This clamping method completely restricts the axial movement of the limiting roller 44, avoiding the position deviation of the roller caused by the gap 102 between the support sleeve and the limiting roller 44. Through the cooperation of the mandrel 42 and the support sleeve, the installation spacing of the limiting roller 44 is accurately controlled, thereby eliminating the vertical floating and jumping of the shuttle caused by the excessive spacing of the roller assembly. Compared with the prior art, in the prior art, two rollers are symmetrically installed on the support shaft and have a fixed spacing, but the roller spacing cannot be dynamically adjusted according to the assembly error or wear, resulting in insufficient stability of the shuttle in the vertical direction. The axial positioning structure of the mandrel 42 and the support sleeve in the present scheme 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 the vertical displacement of the shuttle during movement. Through the above technical scheme, the present application can accurately control the axial installation position of the limiting roller 44, eliminate the gap 102 caused by the assembly error or wear of the roller assembly, avoid the vertical floating or jumping of the shuttle during circular motion, ensure the stability of the running track of the shuttle, and further improve the knitting 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. In order not to affect the rotation of the limiting roller 44, the limiting roller 44 can be designed to include embedded upper and lower bearings 441 and 442. The inner rings of the upper and lower bearings 441 and 442 are matched with the mandrel 42. The upper support sleeve 43 extends into the top end of the limiting roller 44 and abuts against the inner ring of the upper bearing 441. The lower support sleeve 45 extends into the bottom end of the limiting roller 44 and abuts against the inner ring of the lower bearing 442. The upper and lower bearings 441 and 442 refer to two rolling bearings arranged inside the limiting roller 44, which can be implemented by deep groove ball bearings or angular contact bearings to reduce the rotational friction resistance between the limiting roller 44 and the mandrel 42. The inner ring matched with the mandrel 42 means that the inner ring of the bearing is in interference fit or transition fit with the mandrel 42, which can be implemented by hot mounting process or press mounting process to keep the bearing inner ring and the mandrel 42 relatively stationary. The upper and lower support sleeves 43 and 45 refer to annular parts sleeved on both ends of the mandrel 42, which can be formed by metal materials and used to apply axial pressure to the bearing inner ring. Abutting against the bearing inner ring means that the end face of the support sleeve is in rigid contact with the end face of the bearing inner ring, which can be ensured by machining to make the end face flatness, so that there is no gap between the support sleeve and the bearing inner ring. Specifically, after the bearing inner ring is fixed with the mandrel 42, the limiting roller 44 realizes rotational freedom through the bearing outer ring. The upper support sleeve 43 presses the upper bearing 441 inner ring downward, and the lower support sleeve 45 presses the lower bearing 442 inner ring upward, forming a bidirectional axial constraint. When the limiting roller 44 is subjected to an axial force, the bearing inner ring is limited in displacement by the support sleeve, avoiding the whole bearing to shift along the mandrel 42. The fixed fit of the mandrel 42 and the bearing inner ring ensures the effective transmission of rotational torque, and the rigid contact of the support sleeve and the bearing inner ring forms an axial positioning reference. Compared with the prior art, the roller in the traditional structure is only axially positioned by a single bearing or a sliding sleeve, and there is a gap 102 accumulated to cause axial shift. The present scheme adopts a double-sided bearing combined with a bidirectional support sleeve structure to eliminate the axial assembly gap 102. The rigid contact of the bearing inner ring and the support sleeve forms double limiting, and the axial positioning stiffness is improved by about 40%. Through the above technical scheme, the axial displacement of the limiting roller 44 on the mandrel 42 is effectively suppressed, and the roller axial shift is controlled within 0.05 mm, avoiding the vertical jumping of the shuttle caused by the roller shift. The rigid contact of the bearing inner ring and the support sleeve forms a stable axial constraint, while keeping the roller rotating flexibility, so that the shuttle running track deviation is reduced to below 0.1 mm.

[0037] Although the wear resistance of the supporting roller 400 is good and the service life is high, compared with the circular weaving machine product, it still belongs to the vulnerable part, therefore, in order to facilitate the replacement of each part on the mandrel 42, the top end of the mandrel 42 can be designed to extend upwardly out of the upper door ring 200, the bottom end of the mandrel 42 can be designed to extend downwardly out of the lower door ring 300, and the two ends of the mandrel 42 are fixed by the fastener 421 to axially position the upper door ring 200 and the lower door ring 300 to limit the roller 44. The mandrel 42 refers to a rigid support shaft that penetrates the upper door ring 200, the lower door ring 300 and the limiting roller 44, and can be specifically made of high-strength alloy steel for transmitting axial clamping force and forming a symmetrical constraint path. The fastener 421 refers to a connecting component for fixing the two ends of the mandrel 42, which can be specifically a bolt and nut combination structure for eliminating assembly gap 102 by adjusting the pre-tightening force. The upper door ring 200 and the lower door ring 300 refer to the upper and lower rigid frames of the door ring assembly, and the limiting roller 44 is pressed between the two by the clamping force applied by the fastener 421 at the two ends of the mandrel 42. Specifically, the top end of the mandrel 42 extends upwardly and penetrates the upper door ring 200, the bottom end extends downwardly and penetrates the lower door ring 300, and the two ends are locked and fixed by the bolt and nut. When the fastener 421 is tightened, the upper door ring 200 and the lower door ring 300 are subjected to opposite forces, which generate an axial pressing force on the limiting roller 44. Since the two ends of the mandrel 42 are rigidly fixed, the limiting roller 44 cannot move axially between the upper and lower door rings 300, thereby eliminating displacement caused by the installation gap 102 or dynamic load. The symmetrical extension design of the mandrel 42 uniformly distributes the clamping force, avoiding the unilateral fixation caused by the unilateral fixation. By adjusting the pre-tightening force of the fastener 421, the assembly tolerance between the supporting roller 400 and the door ring can be further compensated to ensure the axial positioning accuracy. Compared with the prior art, the roller assembly in the traditional door ring structure is only axially positioned by unilateral fixation or local clamping, which is easy to cause gap 102 due to vibration or wear, resulting in change of roller spacing. The present scheme applies a bidirectional clamping force by the symmetrical extension of the two ends of the mandrel 42 to form a rigid axial constraint, effectively inhibiting the movement of the supporting roller 400, and actively eliminating the assembly gap 102 by pre-tightening force adjustment, significantly improving the axial positioning reliability. Through the above technical scheme, the present application can avoid the change of roller spacing caused by axial displacement of the supporting roller 400 during operation, thereby preventing the shuttle from floating and jumping in the vertical direction, ensuring the smooth running of the shuttle along the circumferential track, and improving the weaving quality stability. When replacing the parts on the mandrel 42, the fastener 421 at the bottom end of the mandrel 42 can be removed, and then the mandrel 42 can be pulled out as a whole upwardly, or the fastener 421 at the top end of the mandrel 42 can be removed, and then the mandrel 42 can be pulled out as a whole downwardly, which is very convenient.

[0038] The wear-resistant flexible sleeve 41 comprises an upper ring body 411 and a lower ring body 412, and the recessed section 404 comprises an upper taper surface 4041, a cylindrical surface 4042 and a lower taper surface 4043 from top to bottom. The upper ring body 411 is fixed to the upper taper surface 4041 and covers at least part of the cylindrical surface 4042 downward, and the upper limiting surface 402 is arranged on the upper ring body 411. The lower ring body 412 is fixed to the lower taper surface 4043 and covers at least part of the cylindrical surface 4042 upward, and the lower limiting surface 403 is arranged on the lower ring body 412. The upper ring body 411 refers to a split wear-resistant structure covering the upper taper surface 4041 of the support roller 400 and extending to the top of the cylindrical surface 4042. Specifically, the rubber or polyurethane material can be fixed to the upper taper surface 4041 and the cylindrical surface 4042 by injection molding process. The axial constraint force generated by the taper angle enhances the contact stability of the upper ring body 411 and the support roller 400. The lower ring body 412 refers to a symmetrical split structure covering the lower taper surface 4043 of the support roller 400 and extending to the bottom of the cylindrical surface 4042. Specifically, the same material and process as the upper ring body 411 can be used for fixation. The axial displacement of the lower ring body 412 is limited by the inclination angle of the lower taper surface 4043, and the upper ring body 411 forms a two-way covering of the cylindrical surface 4042. The composite curved surface structure composed of the upper taper surface 4041, the cylindrical surface 4042 and the lower taper surface 4043 refers to the three-section geometry of the recessed section 404 of the support roller 400. Specifically, the continuous transition curved surface can be formed by turning, and the combination of the taper and the cylindrical surface 4042 realizes precise positioning and stress dispersion of the wear-resistant flexible sleeve 41. Specifically, the upper ring body 411 is fixed on the upper taper surface 4041 and extends downward to cover the top area of the cylindrical surface 4042. The axial component force generated by the taper angle prevents the upper ring body 411 from separating upward during the shuttle operation, and the covered cylindrical surface 4042 enlarges the contact area to disperse the vertical load. The lower ring body 412 is fixed on the lower taper surface 4043 in a symmetrical manner and extends upward to cover the bottom area of the cylindrical surface 4042. The reverse axial component force generated by the inclination angle of the lower taper surface 4043 restricts the downward displacement of the lower ring body 412, and the upper ring body 411 forms a two-way covering of the cylindrical surface 4042, eliminating the risk of axial displacement of the wear-resistant flexible sleeve 41 in high-speed friction. The upper limiting surface 402 and the lower limiting surface 403 are independently arranged on the upper ring body 411 and the lower ring body 412, respectively. When the limiting surface fails due to long-term wear in a local area, only the corresponding ring body needs to be replaced to restore the limiting function, avoiding the replacement of the entire wear-resistant flexible sleeve 41. The composite curved surface structure decomposes the impact force into axial and radial components through the taper angle when the wear-resistant flexible sleeve 41 bears vertical impact, reduces the internal stress concentration of the material, and improves the structural durability. Compared with the prior art, the traditional integral wear-resistant flexible sleeve 41 is directly sleeved on the cylindrical recessed section 404 and relies only on friction to resist axial displacement, which is prone to displacement or local wear due to stress concentration during high-speed operation.The present scheme uses the axial constraint force generated by the conical surface to enhance the fixing effect of the sleeve body, and the upper and lower ring bodies 412 form mechanical limiting in two directions by covering the cylindrical surface 4042, effectively inhibiting axial displacement. In addition, the split structure allows local replacement of worn parts, significantly reducing maintenance costs compared to overall replacement. Through the above technical scheme, the present application solves the problems of axial displacement and local wear caused by the unstable structure of the wear-resistant flexible sleeve 41. Through the synergistic effect of the split ring body and the composite curved surface, the limiting groove 401 and the limiting protrusion 11 can maintain precise cooperation for a long time, prolong the service life of the wear-resistant flexible sleeve 41, and maintain the stability of the shuttle boat running track. The upper ring body 411 and the lower ring body 412 can also be a one-piece structure. In order 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 as a structure with a circular arc chamfer R1, improving the service life of the wear-resistant flexible sleeve 41. Since the upper ring body 411 and the lower ring body 412 both cover part of the cylindrical surface 4042, they can withstand the centrifugal force generated during the movement of the shuttle boat. During the process of continuously contacting and leaving the supporting roller 400 during the circular movement of the shuttle boat, they can withstand impact force well, not only improving the stability of the shuttle boat movement, but also reducing impact noise. They can also share the impact force borne by the upper limiting surface 402 and the lower limiting surface 403, improving the overall life 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 smallest part of the diameter of the limiting roller 44, in order to ensure the structural strength and service life of the support roller 400, the diameter D of the cylindrical surface 4042 should not be less than 20 mm. Since the limiting roller 44 is shaped like a thick end and a thin middle, considering the embedded device of the upper bearing 441 and the lower bearing 442, the cylindrical surface 4042 should not be too small, otherwise the upper limiting surface 402 and the lower limiting surface 403 are too inclined, which is not conducive to the movement and cooperation of the limiting protrusion 11. The cylindrical surface 4042 refers to the outer peripheral surface of the support roller 400 that is in contact with the outside of the shuttle, which can be realized by processing a cylindrical structure made of metal material, and the radial support area can be increased by increasing the diameter of the cylindrical surface 4042. Among them, the diameter of not less than 20 mm means that the maximum straight line distance of the cross section of the cylindrical surface 4042 reaches or exceeds this value, which can be realized by increasing the outer diameter of the mandrel 42 or adjusting the thickness of the wear-resistant flexible sleeve 41, to ensure that the roller assembly has sufficient bending stiffness and anti-deformation ability when bearing the load of the shuttle movement. Specifically, the diameter of the cylindrical surface 4042 directly affects the radial bearing capacity of the roller assembly. When the diameter increases, the contact area between the roller and the outside of the shuttle increases, so that the radial load can be uniformly transmitted to the door ring structure through a wider support surface. This design effectively disperses the local stress generated by the movement of the shuttle, avoiding the expansion of the support gap 102 caused by the deformation of the roller. At the same time, the increased diameter of the cylindrical surface 4042 provides sufficient space for the processing of the limiting groove 401, so that the contact area between the limiting protrusion 11 and the limiting groove 401 can maintain a stable matching relationship, thereby forming a more reliable constraint in the vertical direction. Compared with the prior art, the diameter of the cylindrical surface 4042 of the traditional roller assembly is usually less than 20 mm, resulting in insufficient radial support area, which is prone to elastic deformation when the shuttle moves at high speed, and aggravates the vertical floating. By limiting the lower limit of the diameter of the cylindrical surface 4042, the structural rigidity of the roller assembly is strengthened, and the influence of the roller spacing on the floating of the shuttle is significantly inhibited. Through the above technical scheme, the radial support stability of the roller assembly can be enhanced, the vertical jumping of the shuttle caused by the excessive roller spacing can be reduced, the stable posture of the shuttle during circular orbit operation can be ensured, and the interlacing precision of the warp and weft during knitting can be improved.

[0040] The present application also provides a shuttleless wheel circular weaving machine, which comprises the shuttleless wheel door ring assembly of any one of the above-mentioned embodiments, greatly improves the stability of the shuttle movement, improves the weaving quality, is also beneficial to prolong the service life of the support roller, reduces the replacement frequency, is beneficial to ensure the working time of the circular weaving machine, and improves the weaving efficiency.

[0041] In addition to the above preferred embodiments, the present application also has other embodiments, and all other embodiments obtained by those skilled in the art without creative labor based on the embodiments in the present application belong to the scope of the present application.

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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