False twister spindle and false twister unit
By simplifying the design of the false twister spindle assembly, and using a shaft body, outer cylinder, bearings, balls, and L-shaped damping ring, the problems of complex assembly and high cost are solved, achieving higher operating accuracy and stability.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- SCHAEFFLER TECHNOLOGIES AG & CO KG
- Filing Date
- 2025-04-24
- Publication Date
- 2026-05-12
Smart Images
Figure CN224227325U_ABST
Abstract
Description
Technical Field
[0001] This utility model relates to the field of textile machinery technology. Specifically, this utility model relates to a false twister spindle and a false twister unit. Background Technology
[0002] In textile machinery, texturing machines are used for texturing synthetic fibers. A texturing machine comprises multiple sets of false twister units. In related technologies, each false twister unit has three false twister spindles. The false twister spindles rotate at the same speed via pulleys mounted at one axial end. Friction discs are mounted on the false twister spindles.
[0003] The false twister spindle rotates at high speed during operation. To reduce vibration during operation, damping elements are required in the false twister spindle shaft. The assembly process of the false twister spindle shaft in related technologies is very complex and the manufacturing cost is high. Furthermore, axial clearance of the bearing can cause misalignment and vibration during operation.
[0004] Therefore, there is an urgent need for a false twister spindle and false twister unit that is easy to assemble, relatively low in cost, and can meet the requirements of damping and vibration reduction. Utility Model Content
[0005] To solve the above technical problems, this utility model provides a false twister spindle and a false twister unit.
[0006] In a first aspect, an embodiment of the present invention provides a false twister spindle shaft, comprising: a shaft body, an outer cylinder, a bearing, a plurality of balls, a washer, and an L-shaped damping ring. The outer cylinder is coaxially sleeved on the outer periphery of the shaft body; the bearing is radially disposed between the shaft body and the outer cylinder; the plurality of balls are radially disposed between the shaft body and the outer cylinder, and axially disposed on one side of the bearing; the washer is radially sleeved between the shaft body and the outer cylinder, and axially disposed on the side of the bearing opposite to the balls; the L-shaped damping ring includes an axially extending portion and a radially extending portion, wherein the axially extending portion is radially disposed between the bearing and the outer cylinder, and the radially extending portion is axially disposed between the bearing and the washer.
[0007] According to some alternative embodiments, an O-ring damping ring is provided between the washer and the radial extension.
[0008] According to some optional embodiments, the washer has a receiving groove corresponding to the O-ring damping ring on the side facing the radial extension in the axial direction, and the axial portion of the O-ring damping ring is disposed in the receiving groove.
[0009] According to some alternative embodiments, a disc spring is provided between the washer and the radial extension.
[0010] According to some optional embodiments, at least two disc springs are provided, with adjacent disc springs arranged opposite each other in the axial direction.
[0011] According to some optional embodiments, a first shaft raceway for receiving the plurality of balls is provided on the outer circumference side of the shaft body at a position corresponding to the plurality of balls, and an outer cylinder raceway for receiving the plurality of balls is provided on the inner circumference side of the outer cylinder at a position corresponding to the plurality of balls, so that the plurality of balls are radially supported between the shaft body and the outer cylinder.
[0012] According to some alternative embodiments, in the axial direction, the section of the outer cylinder located on the side of the bearing opposite to the washer has a narrowing section extending radially inward, and the outer cylinder raceway is disposed on the inner circumferential side of the narrowing section.
[0013] According to some alternative embodiments, the outer diameter of the axial extension gradually decreases in the portion axially toward the plurality of balls, forming a damping ring chamfer.
[0014] According to some optional embodiments, the bearing includes bearing rollers and a bearing outer ring; the outer diameter of the bearing outer ring gradually decreases in the axial direction toward the plurality of balls, forming an outer ring chamfer; wherein the damping ring chamfer is formed on the outer periphery of the outer ring chamfer.
[0015] In a second aspect, embodiments of the present invention provide a false twister unit, including at least one false twister spindle as described in any of the above embodiments.
[0016] With the false twister spindle in the above embodiments, firstly, one of the support members can use a conventional bearing, thus simplifying the design of the false twister spindle, making the assembly process easier, and reducing manufacturing costs. Secondly, the other support member has raceways directly formed on the outer circumference of the shaft body and the inner circumference of the outer cylinder, with the balls positioned therein providing direct radial support between the shaft body and the outer cylinder without clearance, thereby improving the running accuracy of the false twister spindle. Furthermore, the L-shaped damping ring can simultaneously provide axial and radial damping forces to the bearing, further simplifying the design and reducing manufacturing costs. Moreover, arranging O-rings or disc springs on the axially outer sides of the two support members, with the two bearing raceways arranged in an X-shape, can eliminate axial clearance in the false twister bearing. Additionally, the bearing outer ring has an outer ring chamfer, and correspondingly, the axial extension of the L-shaped damping ring has a damping ring chamfer, thus facilitating the interference fit of the bearing and the L-shaped damping ring together onto the radially inner side of the outer cylinder, reducing the risk of damage to the L-shaped damping ring. Attached Figure Description
[0017] To more clearly illustrate the technical solutions of the embodiments of this utility model, the drawings used in the description of the embodiments of this utility model will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.
[0018] Figure 1 A cross-sectional view of the false twister spindle shaft according to some embodiments of the present invention is shown;
[0019] Figure 2 A partially enlarged cross-sectional view of the false twister spindle according to some embodiments of the present invention is shown;
[0020] Figure 3 A cross-sectional view of the false twister spindle according to some other embodiments of the present invention is shown;
[0021] Figure 4 A partially enlarged cross-sectional view of the false twister spindle according to other embodiments of the present invention is shown; and
[0022] Figure 5 A partially enlarged cross-sectional view of the false twister spindle according to some other embodiments of the present invention is shown. Detailed Implementation
[0023] To make the objectives, technical solutions, and advantages of the embodiments of this disclosure clearer, the technical solutions of the embodiments of this disclosure will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of this utility model. All other embodiments obtained by those skilled in the art based on the described embodiments of this utility model are within the protection scope of this utility model.
[0024] According to an embodiment of this utility model, a false twister spindle is provided. The false twister spindle is used in a texturing machine in textile machinery. The texturing machine is used in the texturing process of synthetic fibers. The texturing machine includes multiple sets of false twister units. Each false twister unit has three false twister spindles. The three false twister spindles rotate at the same speed via pulleys mounted at one axial end. A friction disc is mounted on the false twister spindle. The false twister spindle rotates at high speed during operation; to reduce vibration during operation, damping elements are required in the false twister spindle. This utility model proposes a false twister spindle with simplified design, easy assembly, and lower cost.
[0025] Figure 1 A cross-sectional view of the false twister spindle shaft according to some embodiments of the present invention is shown; Figure 2A partially enlarged cross-sectional view of the false twister spindle according to some embodiments of the present invention is shown. See also Figure 1 and Figure 2 As shown, the false twister spindle 100 provided according to an embodiment of the present invention includes: a shaft body 1, an outer cylinder 7, a bearing 6, multiple balls 8, a washer 3, and an L-shaped damping ring 5.
[0026] The outer cylinder 7 is coaxially sleeved on the outer circumference of the shaft.
[0027] Bearing 6 is radially positioned between shaft 1 and outer cylinder 7 to provide radial support between them. Specifically, bearing 6 can be fitted onto shaft 1 with an interference fit. Furthermore, bearing 6 can be a deep groove ball bearing, or other types of bearings such as cylindrical roller bearings, or a bearing with its inner ring omitted, where the radial inner side of its rollers is directly supported on shaft 1. Any bearing that provides radial support is acceptable and is not limited here.
[0028] Multiple balls 8 are radially disposed between the shaft 1 and the outer cylinder 7 to provide radial support between the shaft 1 and the outer cylinder 7, and are axially disposed on one side of the bearing 6. In this way, the bearing 6 and the multiple balls 8 are arranged axially at intervals as two support members, which together provide radial support for the shaft 1 and the outer cylinder 7.
[0029] The washer 3 is radially fitted between the shaft 1 and the outer cylinder 7, and axially positioned on the side of the bearing 6 away from the ball 8. Specifically, the washer 3 can be assembled in the inner hole of the outer cylinder 7 by interference fit to provide axial positioning for the bearing 6.
[0030] The L-shaped damping ring 5 includes an axial extension 51 and a radial extension 52. The axial extension 51 is radially disposed between the bearing 6 and the outer cylinder 7, and the radial extension 52 is axially disposed between the bearing 6 and the washer 3. The L-shaped damping ring 5 can be made of an elastic material such as plastic or rubber to provide radial and axial damping for the false twister spindle 100. Specifically, the outer cylinder 7 can be fitted onto the outer periphery of the axial extension 51 by an interference fit, and the axial extension 51 provides radial damping between the bearing 6 and the outer cylinder 7. The radial extension 52 can abut against one axial end of the bearing 6 to provide axial damping for the bearing 6.
[0031] like Figure 1 and Figure 2 As shown, the false twister spindle 100 also includes a retaining ring 2, which is sleeved on the shaft body 1 and disposed at the axial end of the washer 3 away from the bearing 6. Furthermore, there may be a gap between the retaining ring 2 and the washer 3 to form a labyrinth seal. Specifically, as... Figure 2As shown, the retaining ring 2 covers the washer 3 in the axial direction, so that the projections of the retaining ring 2 and the washer 3 in the radial direction coincide, and a small L-shaped gap is formed between the retaining ring 2 and the washer 3 to achieve gap sealing between the retaining ring 2 and the washer 3.
[0032] In addition, such as Figure 1 and Figure 2 As shown, the false twister spindle 100 also includes a pulley 9, which is sleeved on the other axial end of the shaft 1 away from the retaining ring 2. The pulley 9 can be a gear or a timing belt, used to rotate multiple false twister spindles 100 at the same speed via the pulley 9 mounted on one axial end.
[0033] In some alternative embodiments, such as Figure 1 and Figure 2 As shown, an O-ring damping ring 41 is provided between the washer 3 and the radial extension 52. The O-ring damping ring 41 can be made of elastic materials such as plastic or rubber. The O-ring damping ring 41 can provide axial damping to the bearing 6 by contacting and pressing against the radial extension 52.
[0034] In some alternative embodiments, such as Figure 2 As shown, the washer 3 has a receiving groove 31 corresponding to the O-ring damping ring 41 on the side facing the radial extension 52 in the axial direction. In the axial direction, part of the O-ring damping ring 41 is disposed in the receiving groove 31, and the other part of the O-ring damping ring 41 protrudes from the washer 3. In this way, the O-ring damping ring 41 can be fixedly installed on the axial side of the washer 3, and can provide axial damping to the bearing 6 through the L-shaped damping ring 5.
[0035] Figure 3 A cross-sectional view of the false twister spindle according to other embodiments of the present invention is shown; and Figure 4 A partially enlarged cross-sectional view of the false twister spindle according to other embodiments of the present invention is shown. See also Figure 3 and Figure 4 As shown, in some optional embodiments, a disc spring 42 is provided between the washer 3 and the radial extension 52 to replace the O-ring damping ring 41 in the above embodiments.
[0036] Specifically, such as Figure 4 As shown, the disc spring 42 is sleeved on the shaft 1 and is located axially between the washer 3 and the radial extension 52. The disc spring 42 abuts against the radial extension 52, thereby providing axial damping to the bearing 6.
[0037] The disc spring 42 can be provided in at least two configurations, with adjacent disc springs 42 arranged opposite each other in the axial direction. For example... Figure 4As shown, two disc springs 42 are provided, and the two disc springs 42 are arranged back to back, so that the disc springs 42 provide axial preload and damping force to the bearing 6 via the radial extension 52. It can be understood that more disc springs 42 can be provided, and in more disc springs 42, every two adjacent disc springs 42 are arranged back to back.
[0038] In some alternative embodiments, such as Figures 1 to 4 As shown, a first shaft raceway 11 for receiving the plurality of balls 8 is provided on the outer circumference side of the shaft 1 at a position corresponding to the plurality of balls 8, and an outer cylinder raceway 71 for receiving the plurality of balls 8 is provided on the inner circumference side of the outer cylinder 7 at a position corresponding to the plurality of balls 8, so that the plurality of balls 8 are radially supported between the shaft 1 and the outer cylinder 7.
[0039] In this embodiment, the shaft 1 and the outer cylinder 7 are directly used as the inner ring and outer cylinder of the support member formed by the ball bearings 8, without any other support structure. This ensures that the support member will not have any gaps in the radial direction, thereby improving the running accuracy of the false twister spindle 100.
[0040] In some alternative embodiments, such as Figures 1 to 4 As shown, in the axial direction, the section of the outer cylinder 7 located on the side of the bearing 6 away from the washer 3 has a narrowing section 72 extending radially inward, and the outer cylinder raceway 71 is disposed on the inner circumferential side of the narrowing section 72.
[0041] In this way, the axial end of the bearing 6 is provided with axial damping by the O-ring damping ring 41 or the disc spring 42 and the radial extension 52 of the L-shaped damping ring 5, so that the false twister spindle 100 can remain stable when rotating at high speed and reduce vibration.
[0042] Figure 5 A partially enlarged cross-sectional view of the false twister spindle shaft according to some other embodiments of the present invention is shown. In some optional embodiments, the bearing 6 includes at least bearing rollers 61 and bearing outer rings 62. Optionally, the bearing 6 can be as follows: Figure 2 and Figure 4 The complete bearing shown, including bearing roller 61, bearing outer ring 62, and bearing inner ring, can also be as follows: Figure 5 The image shows a portion of the bearing including bearing rollers 61 and outer ring 62, while omitting the inner ring. In contrast, as shown in... Figure 5 In the embodiment shown, the bearing 6 omits the inner ring, and the radially inner side of the bearing roller 61 is directly supported on the shaft 1. Therefore Figure 5 The bearing 6 shown can also provide radial support between the shaft 1 and the outer cylinder 7.
[0043] Furthermore, such as Figure 5As shown, in an embodiment where the bearing 6 omits the inner ring, a second shaft raceway 12 that receives the circumferentially extending bearing roller 61 can be provided on the outer circumferential side of the shaft 1 at a position corresponding to the bearing 6. The radially inner side of the first bearing roller 61 in the bearing 6 can be provided in the second shaft raceway 12 to directly contact and support the shaft 1.
[0044] In some alternative embodiments, such as Figure 5 As shown, the axial extension 51 is axially directed toward the plurality of balls 8 (towards the axial inward side, i.e.) Figure 5 The outer diameter of the portion (facing right) gradually decreases, forming a damping ring chamfer 511. During assembly, the bearing 6 is placed within the L-shaped damping ring 5. The bearing 6, together with the L-shaped damping ring 5, is located radially inside the outer cylinder 7 and is interference-fitted with the L-shaped damping ring 5 and the outer cylinder 7.
[0045] By providing a damping ring chamfer 511 to the axial extension 51 of the L-shaped damping ring 5, the installation process of the bearing 6 and the L-shaped damping ring 5 being interference-fitted together to the radial inner side of the outer cylinder 7 is made easier, and the risk of damage to the L-shaped damping ring, which is made of elastic material such as rubber, during the interference fit process can be greatly reduced.
[0046] In some alternative embodiments, such as Figure 5 As shown, the outer ring 62 of the bearing is axially oriented towards the plurality of balls 8 (oriented axially inward, i.e.) Figure 5 The outer diameter of the portion (facing right) gradually decreases, forming an outer chamfer 621; wherein, the damping ring chamfer 511 is formed on the outer periphery of the outer chamfer 621.
[0047] The bearing outer ring 62 is provided with an outer ring chamfer 621. This allows the L-shaped damping ring 5 to be formed on the bearing outer ring 62 of the bearing 6 through a vulcanization process, so that the L-shaped damping ring 5 can correspond to the outer ring chamfer 621 to form a damping ring chamfer 511. The outer ring chamfer 621 facilitates the direct formation of the damping ring chamfer 511 by the L-shaped damping ring 5 through the vulcanization process, simplifying the process flow.
[0048] Furthermore, in some alternative embodiments, such as Figure 5As shown, in order to strengthen the radial interference fit between the outer cylinder 7 and the L-shaped damping ring 5, a damping ring mating portion 73 extending radially inward (i.e., with a decreasing inner diameter) is provided on the inner circumference of the section of the outer cylinder 7 corresponding to the axial extension portion 51 of the L-shaped damping ring 5. In this case, in the axial direction toward the washer 3, the axial dimension of the axial extension portion 51 should be greater than the axial dimension of the damping ring mating portion 73, and the axial end of the axial extension portion 51 should extend beyond the axial end of the damping ring mating portion 73, so that the washer 3, or the O-ring damping ring 41, or the disc spring 42 on the axial side can ensure axial contact with the radial extension portion 52 without being interfered with by the damping ring mating portion 73.
[0049] The present invention also provides a false twister unit, which includes at least one false twister spindle 100 as described in any of the above embodiments.
[0050] With the false twister spindle 100 in the above embodiments, firstly, one of the support members can use a conventional bearing, thus simplifying the design of the false twister spindle 100, making the assembly process easier, and reducing manufacturing costs. Secondly, the other support member has its raceway directly formed on the outer circumference of the shaft body 1 and the inner circumference of the outer cylinder 7, with the balls 8 positioned therein providing direct radial support between the shaft body 1 and the outer cylinder 7 without gaps, thereby improving the running accuracy of the false twister spindle 100. Furthermore, the L-shaped damping ring 5 can simultaneously provide axial and radial damping forces to the bearing 6, further simplifying the design and reducing manufacturing costs. Moreover, by arranging the O-ring damping ring 41 or disc spring 42 on the axially outer side of the two support members, and with the two bearing raceways arranged in an X-shape, the axial clearance of the false twister spindle bearing can be eliminated. In addition, the outer ring 62 of the bearing is provided with an outer ring chamfer 621, and correspondingly, the axial extension 51 of the L-shaped damping ring 5 is provided with a damping ring chamfer 511. Therefore, it is easier for the bearing 6 and the L-shaped damping ring 5 to be interference-fitted together to the radial inner side of the outer cylinder 7, reducing the risk of damage to the L-shaped damping ring 5.
[0051] While possible embodiments have been described exemplarily in the foregoing description, it should be understood that numerous variations of the embodiments exist through combinations of all known and readily conceived technical features and implementation methods. Furthermore, it should be understood that the exemplary embodiments are merely examples and do not in any way limit the scope, application, or construction of this invention. The foregoing description is more intended to provide those skilled in the art with technical guidance for transforming at least one exemplary embodiment, wherein various changes, particularly regarding the function and structure of the components, can be made without departing from the scope of the claims.
[0052] Appendix Label Table
[0053] 100. False twister spindle
[0054] 1. Shaft body; 11. First shaft body raceway; 12. Second shaft body raceway;
[0055] 2. Retaining ring;
[0056] 3. Washers;
[0057] 41. O-ring damping ring; 42. Disc spring;
[0058] 5. L-shaped damping ring; 51. Axial extension; 52. Radial extension; 511. Damping ring chamfer;
[0059] 6. Bearing; 61. Bearing roller; 62. Bearing outer ring; 621. Outer ring chamfer 6;
[0060] 7. Outer cylinder; 71. Outer cylinder raceway; 72. Narrowing section; 73. Damping ring mating part;
[0061] 8. Ball bearings;
[0062] 9. Pulley.
Claims
1. A false twister spindle, characterized in that, include: Shaft (1), The outer cylinder (7) is coaxially sleeved on the outer periphery of the shaft (1); A bearing (6) is radially disposed between the shaft (1) and the outer cylinder (7); Multiple balls (8) are arranged radially between the shaft (1) and the outer cylinder (7) and axially on one side of the bearing (6); Washer (3) is fitted radially between the shaft (1) and the outer cylinder (7) and is axially positioned on the side of the bearing (6) away from the ball (8); as well as L-shaped damping ring (5) includes an axial extension (51) and a radial extension (52), wherein the axial extension (51) is radially disposed between the bearing (6) and the outer cylinder (7), and the radial extension (52) is axially disposed between the bearing (6) and the washer (3).
2. The false twister spindle according to claim 1, characterized in that, An O-ring (41) is provided between the washer (3) and the radial extension (52).
3. The false twister spindle according to claim 2, characterized in that, The washer (3) has a receiving groove (31) corresponding to the O-ring damping ring (41) on the side facing the radial extension (52) in the axial direction, and the axial portion of the O-ring damping ring (41) is disposed in the receiving groove (31).
4. The false twister spindle according to claim 1, characterized in that, A disc spring (42) is provided between the washer (3) and the radial extension (52).
5. The false twister spindle according to claim 4, characterized in that, At least two disc springs (42) are provided, and two adjacent disc springs (42) are arranged opposite each other in the axial direction.
6. The false twister spindle according to claim 1, characterized in that, The outer circumference of the shaft (1) is provided with a first shaft raceway (11) corresponding to the position of the plurality of balls (8), and the inner circumference of the outer cylinder (7) is provided with an outer cylinder raceway (71) corresponding to the position of the plurality of balls (8), so that the plurality of balls (8) are radially supported between the shaft (1) and the outer cylinder (7).
7. The false twister spindle according to claim 6, characterized in that, In the axial direction, the section of the outer cylinder (7) located on the side of the bearing (6) away from the washer (3) has a narrowed section (72) extending radially inward, and the outer cylinder raceway (71) is disposed on the inner circumferential side of the narrowed section (72).
8. The false twister spindle according to claim 1, characterized in that, The outer diameter of the axial extension (51) gradually decreases in the axial direction toward the plurality of balls (8), forming a damping ring chamfer (511).
9. The false twister spindle according to claim 8, characterized in that, The bearing (6) includes bearing rollers (61) and bearing outer ring (62); the outer diameter of the bearing outer ring (62) gradually decreases in the axial direction toward the plurality of balls (8), forming an outer ring chamfer (621); wherein the damping ring chamfer (511) is formed on the outer periphery of the outer ring chamfer (621).
10. A false twister unit, characterized in that, It includes at least one false twister spindle (100) as claimed in any one of claims 1 to 9.