Abstract
A support is provided for a flexible bend in a revolving flat card, the flat card having a cylinder and a cylinder axis. The support has at least three bearing points, with each bearing point comprising a bearing bolt and an adjusting lever. At each bearing point, the flexible bend is held on the bearing bolt such that a rotational motion of the bearing bolt brings about a displacement of the flexible bend radially with respect to the cylinder axis. Each bearing bolt has a bearing bolt axis, a fastening portion, a moving portion, and a contact surface for contact with the flexible bend. The contact surface is formed by a surface that spirals around the bearing bolt axis.
Claims
1. A support for a flexible bend in a revolving flat card, the flat card having a cylinder and a cylinder axis, the support comprising: at least three bearing points, each bearing point further comprising a bearing bolt and an adjusting lever, wherein at each bearing point, the flexible bend is held on the bearing bolt such that a rotational motion of the bearing bolt brings about a displacement of the flexible bend radially with respect to the cylinder axis; each bearing bolt comprising a bearing bolt axis, a fastening portion, a moving portion, and a contact surface for contact with the flexible bend; wherein the contact surface is formed by a surface that spirals around the bearing bolt axis; and wherein the adjusting lever is held on the moving portion of each of the bearing bolts, and wherein all of the adjusting levers are connected to a common slider.
2. The support according to claim 1, wherein the spiral surface is an Archimedean spiral and, therefore, a decrease or an increase in a radial spacing distance (B) of the contact surface from the bearing bolt axis during a rotation of the bearing bolt is linear with respect to a rotational angle of the bearing bolt.
3. The support according to claim 1, wherein the spiral surface is defined such that there is a linear dependence between a rotational angle () of the bearing bolt and a spacing distance (A) between the bearing bolt axis and the flexible bend in the direction of movement of the flexible bend.
4. The support according to claim 1, wherein a radial spacing distance (B) of the contact surface from the bearing bolt axis decreases or increases by 5% to 30% in a helical manner along a course of the contact surface during at least one-half of a circumference of the bearing bolt.
5. The support according to claim 1, wherein the fastening portion is disposed between the moving portion and the contact surface in the direction of the bearing bolt axis (25).
6. The support according to claim 5, wherein the fastening portion is split by the contact surface disposed within the fastening portion.
7. The support according to claim 1, wherein the adjusting lever is non-rotatably held on the bearing bolt by a releasable locking mechanism.
8. The support according to claim 1, wherein at least part of a circumference of the moving portion of the bearing bolt is provided with a tooth system.
9. The support according to claim 8, further comprising an adjusting element configured with the adjusting lever, the adjusting element in combination with the tooth system forming a worm gear.
10. The support according to claim 1, wherein the contact surface has a maximum radial spacing distance (Bmax) from the bearing bolt axis (25) that is not greater than one-half the diameter (D) of the bearing bolt at the fastening portion.
11. The support according to claim 1, wherein each adjusting lever is held by a guide pin in the slider in a radially oriented guide groove.
12. The support according to claim 1, wherein the slider is provided with a drive.
13. A revolving flat card, comprising: a cylinder having cylinder clothing thereon; a revolving flat assembly comprising a plurality of interconnected revolving flats guided on a flexible bend; and a support for the flexible bend according to claim 1.
Description
BRIEF DESCRIPTION OF THE DRAWINGS
(1) The invention is described in greater detail in the following on the basis of exemplary embodiments and with reference to drawings.
(2) FIG. 1 shows a schematic illustration of a side view of a revolving flat card according to the prior art;
(3) FIG. 2 shows a schematic illustration of one view of an embodiment of a bearing point according to the invention;
(4) FIG. 3 shows a schematic sectional illustration of one embodiment at the point Z-Z according to FIG. 2;
(5) FIG. 4 shows a schematic sectional illustration at the point X according to FIG. 3;
(6) FIG. 5 shows a schematic sectional illustration at the point Y according to FIG. 3;
(7) FIG. 6 shows a schematic sectional illustration of another embodiment at the point Z-Z according to FIG. 2; and
(8) FIG. 7 shows a schematic illustration of one embodiment of a bearing point.
DETAILED DESCRIPTION
(9) Reference will now be made to embodiments of the invention, one or more examples of which are shown in the drawings. Each embodiment is provided by way of explanation of the invention, and not as a limitation of the invention. For example features illustrated or described as part of one embodiment can be combined with another embodiment to yield still another embodiment. It is intended that the present invention include these and other modifications and variations to the embodiments described herein.
(10) A known revolving flat card 1 is illustrated in FIG. 1, wherein tufts are fed from a feed chute 2 to a fiber feed device 3 and a downstream cylinder 4. The revolving flat card 1 comprises a single cylinder 4 (main cylinder or so-called cylinder), which is rotatably supported in a machine frame 5. The cylinder 4 interacts, in a known manner, with a revolving flat assembly 6, a fiber feed device 3, and a fiber removal system 8, wherein the latter comprises, in particular, a so-called doffer 9. Carding elements and fiber-routing elements, which are not shown in greater detail here, can be disposed between the revolving flat arrangement 6, the fiber feed device 3, and the fiber removal system 8. The fiber removal system 8 conveys the sliver 10 to a schematically indicated sliver coiling system 11.
(11) A plurality of revolving cards 13 is provided at the aforementioned revolving flat assembly 6, wherein only a single revolving card 13 is schematically depicted in FIG. 1. Revolving flat assemblies 6 that are common today comprise multiple, narrowly spaced revolving flats 13, which revolve. For this purpose, the revolving flats 13 are carried, near their respective end faces, by endless belts 12 and are moved counter to or in the direction of rotation of the cylinder 4. The support takes place, in this connection, on flexible bends 7 on the underside of the revolving flat assembly 6. The revolving flats 13 slide on the flexible bend 7 as they are guided along the cylinder surface.
(12) FIG. 2 shows a schematic illustration of one embodiment of a bearing point 20 of a flexible bend 7 according to the invention. The flexible bend 7 is shown in a sectional view and is supported on multiple bearing points 20. At the bearing point 20, the flexible bend 7 is held on a bearing bolt 21. The bearing bolt 21 is shown in a sectional view such that the contact surface 24, on which the flexible bend 20 rests, is shown. The contact surface 24 of the bearing bolt 21 spirals around the bearing bolt axis 25. The bearing bolt axis 25 is the rotational axis of the bearing bolt 21. The bearing bolt 21 is rotatably mounted in the machine frame (not shown), and so the rotational axis, or the bearing bolt axis 25, is held stationary. The adjusting lever 26 is non-rotatably held on the bearing bolt 21. In turn, the adjusting lever 26 is held, by means of a guide pin 30, in a guide groove 34 of a slider 35.
(13) In the event of a tangential movement 36 of the slider 35, all the adjusting levers 26 are rotated by means of their guide pins 34 about the bearing bolt axis 25. Since the adjusting lever 26 is also non-rotatably connected to the bearing bolt 21, the rotational motion of the adjusting lever 26 is transferred to the bearing bolt 21. As a result of the rotational motion of the bearing bolt 21, the spacing distance A of the flexible bend 7 from the bearing bolt axis 25 changes due to the helical contact surface 24 of the bearing bolt. Since the bearing bolt 21 and, therefore, the bearing bolt axis 25 are held stationary in the machine frame, the flexible bend 7 is moved radially away from the bearing bolt axis 25 or toward the bearing bolt axis 25. The direction of movement 37 of the flexible bend 7 is dependent on the rotational direction of the bearing bolt 21 and the arrangement of the helical contact surface 24.
(14) FIG. 3 shows a schematic sectional illustration at the point Z-Z according to FIG. 2 of a view of an embodiment of a bearing point 20 according to the invention. The bearing bolt 21 has a moving portion 22, a fastening portion 23, and a contact surface 24. The flexible bend 7 is supported on the contact surface 24, which has a position-dependent spacing distance A from the bearing bolt axis 25. In the fastening portion 23, the bearing bolt 21 is rotatably mounted in the machine frame 5. In the fastening portion 23, the bearing bolt 21 has a diameter D, which corresponds to at least twice the largest possible spacing distance B of the contact surface 24 from the bearing bolt axis 25 (for the largest possible spacing distance B.sub.max, see FIG. 7). An adjusting lever 26 is disposed in the moving portion 22 of the bearing bolt 21. The adjusting lever 26 is non-rotatably connected to the bearing bolt 21 by means of the locking mechanism 27. At least part of the bearing bolt 21 is provided with a tooth system 28 in the moving portion 22. The adjusting element 29 installed in the adjusting lever 26 engages into this tooth system 28. A guide pin 30 mounted on the adjusting lever 26 is provided for non-rotatably holding the adjusting lever 26. The guide pin 30 is held by the slider 35 (see FIG. 2). When the locking mechanism 27 is released, the adjusting element 29 can be rotated in order to rotate the bearing bolt 21 via the tooth system 28 for manually setting the basic spacing distance A of the contact surface 24 from the bearing bolt axis 25. After the manual basic setting of the bearing point 20, the locking mechanism 27 is engaged and any further displacement of the bearing point 20 is carried out by rotating the adjusting lever 26. The rotation of the adjusting lever 26 is transferred via the locking mechanism 27 directly to the bearing bolt 21.
(15) FIG. 4 shows a schematic sectional illustration at the point X according to FIG. 3. The moving portion 22 of the bearing bolt 21 is shown at the point having the tooth system 28. The tooth system 28 extends over only a portion of the circumference of the bearing bolt 21, specifically over a portion of the circumference that corresponds to the helical shape of the contact surface of the bearing bolt 21. The adjusting element 29 mounted in the adjusting lever 26 engages, via its worm gear, into the tooth system 28, which induces a rotation of the bearing bolt 21 when the adjusting element 29 is rotated. The adjusting lever 26 is prevented from rotating by the guide pin 30. The adjusting element 29 is provided with a head, which is designed for use with a tool or which can be operated by hand.
(16) FIG. 5 shows a schematic sectional illustration at the point Y according to FIG. 3. The moving portion 22 of the bearing bolt 21 is shown at the point having the locking mechanism 27 of the adjusting lever 26. The locking mechanism 27 consists of two clamping bolt halves 31, 32, which are inserted into a hole in the adjusting lever 26. In this case, a first clamping bolt half 31 is introduced from one side of the bearing bolt 21 and a second clamping bolt half 32 is introduced from the opposite side of the bearing bolt 21 into the hole in the adjusting lever 26. The two clamping bolt halves 31, 32 are drawn together by means of a fixing screw 33, whereby the first clamping bolt half 31 is provided with a corresponding inner thread. The two clamping bolt halves 31, 32, in the area of the bearing bolt 21, are provided with a shape corresponding to the bearing bolt, and so drawing the clamping bolt halves 31, 32 together causes the adjusting lever 26 to be non-rotatably held on the bearing bolt 21. The same effect could also be achieved by designing one side of the adjusting lever 26 so as to be elastic and drawing the elastic area of the adjusting lever 26 together with the rigid area of the adjusting lever 26 by means of the fixing screw 33 and thereby non-rotatably connecting the adjusting lever 26 to the bearing bolt 21.
(17) FIG. 6 shows a schematic sectional illustration of another embodiment, at the point Z-Z according to FIG. 2, of a bearing point 20. In contrast to the embodiment according to FIG. 3, the contact surface 24 of the bearing bolt 21 is disposed within the fastening portion 23. The fastening portion 23 adjoins the moving portion 22 and is interrupted by the contact surface 24. The diameter D of the bearing bolt 21, on the side facing the moving portion 22, corresponds to the diameter D according to FIG. 3. On the side of the fastening portion facing away from the moving portion 22, however, the bearing bolt 21 has a smaller diameter d, which is less than twice the minimum spacing distance B.sub.min of the contact surface 24 from the bearing bolt axis (see FIG. 7). The design of the moving portion 22 having the adjusting lever 26 corresponds to the embodiment according to FIG. 3. An adjusting lever 26 is disposed in the moving portion 22 of the bearing bolt 21. The adjusting lever 26 is non-rotatably connected to the bearing bolt 21 via the locking mechanism 27. At least part of the bearing bolt 21 is provided with a tooth system 28 in the moving portion 22. The adjusting element 29 installed in the adjusting lever 26 engages into this tooth system 28. A guide pin 30 mounted on the adjusting lever 26 is provided for non-rotatably holding the adjusting lever 26. The bearing bolt 21 is mounted, via its fastening portion 23, in the machine frame 5 on both sides of the contact surface 24. As a result, the forces applied by the flexible bend 7 onto the bearing bolts 21 in two support positions are absorbed by the machine frame 5 and the bending stress of the bearing bolt 21 is reduced as compared to the embodiment according to FIG. 3.
(18) FIG. 7 shows a schematic illustration of a bearing point 20. The bearing bolt 21 having the helical contact surface 24 is rotatably held in the machine frame, being stationary in its bearing bolt axis 25. The flexible bend 7 rests with its support surface, which is designed as a plane, tangentially on the contact surface 24 of the bearing bolt 21. This contact point 40 determines the spacing distance B.sub.(+) of the contact surface 24 from the bearing bolt axis 25 measured in a plane rotated through the angle with respect to the moving direction 37 of the flexible bend. This spacing distance B.sub.(+) of the flexible bend 7 from the bearing bolt axis 25 is not the same, however, as the radial spacing distance A.sub.() of the contact surface 24 from the bearing bolt axis 25 in the moving direction 37 of the flexible bend 7. Given that the flexible bend 7 has a support surface on a side facing the contact surface 24 of the bearing bolt 21, which support surface is designed as a plane, the flexible bend 7 rests tangentially on the helical contact surface 24 of the bearing bolt 21 on the contact point 40. The contact point 40 of the flexible bend 7 is rotated through an angle with respect to the movement line 41 of the flexible bend 7. The helical contact surface 24 of the bearing bolt 21 is shaped in such a way that, upon rotation of the bearing bolt 21, the spacing distance A.sub.() of the flexible bend 7 changes by an amount that is linearly dependent on the rotational angle . Therefore, when the rotational angle changes, the change in the spacing distance A.sub.() is a multiple of a constant.
(19) According to FIG. 7, the helical contact surface 24 extends over one-half the circumference of the bearing bolt 21. This results in a minimum spacing distance B.sub.(+) which is B.sub.min and a maximum spacing distance B.sub.(+) which is B.sub.max. The difference of B.sub.min and B.sub.max yields the maximum possible displacement of the flexible bend 7 on its movement line 41.
(20) Modifications and variations can be made to the embodiments illustrated or described herein without departing from the scope and spirit of the invention as set forth in the appended claims.
LEGEND
(21) 1 revolving flat card 2 feed chute 3 fiber feed device 4 cylinder 5 machine frame 6 revolving flat assembly 7 flexible bend 8 fiber removal system 9 doffer 10 sliver 11 sliver coiling system 12 endless belt 13 revolving flat 20 bearing point 21 bearing bolt 22 moving portion 23 fastening portion 24 contact surface 25 bearing bolt axis 26 adjusting lever 27 locking mechanism 28 tooth system 29 adjusting element 30 guide pin 31, 32 clamping bolt halves 33 fixing screw 34 guide groove 35 slider 36 tangential movement of the slider 37 direction of movement of the flexible bend 40 contact point 41 movement line of the flexible bend A.sub.() spacing distance of the flexible bend from the bearing bolt axis B.sub.(+) radial spacing distance of the contact surface from the bearing bolt axis B.sub.max maximum spacing distance B B.sub.min minimum spacing distance B D first diameter of the bearing bolt in the fastening portion d second diameter of the bearing bolt in the fastening portion rotational angle of the bearing bolt angle between the contact point and the movement line of the flexible bend
