WO2024074407A1 - Peigne circulaire pour peigneuse - Google Patents

Peigne circulaire pour peigneuse Download PDF

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Publication number
WO2024074407A1
WO2024074407A1 PCT/EP2023/076977 EP2023076977W WO2024074407A1 WO 2024074407 A1 WO2024074407 A1 WO 2024074407A1 EP 2023076977 W EP2023076977 W EP 2023076977W WO 2024074407 A1 WO2024074407 A1 WO 2024074407A1
Authority
WO
WIPO (PCT)
Prior art keywords
base body
balancing element
mass balancing
shaft
circular comb
Prior art date
Application number
PCT/EP2023/076977
Other languages
German (de)
English (en)
Inventor
Helmut Herbst
Friedrich Henninger
Original Assignee
Staedtler + Uhl Kg
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Staedtler + Uhl Kg filed Critical Staedtler + Uhl Kg
Publication of WO2024074407A1 publication Critical patent/WO2024074407A1/fr

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Classifications

    • D—TEXTILES; PAPER
    • D01—NATURAL OR MAN-MADE THREADS OR FIBRES; SPINNING
    • D01G—PRELIMINARY TREATMENT OF FIBRES, e.g. FOR SPINNING
    • D01G19/00—Combing machines
    • D01G19/06—Details
    • D01G19/10—Construction, mounting, or operating features of combing elements

Definitions

  • the invention relates to a circular comb for a combing machine for combing textile fibers and for fastening to a shaft of the combing machine that can rotate about a shaft axis.
  • Circular combs for use in combing machines are known from obvious prior use.
  • a combing set is arranged on a base body of the circular comb, which is in engagement with the fiber tuft of the textile fibers to be combed.
  • the combing set is arranged along at least part of a circumference of the outer section of the base body, thereby defining an active combing area.
  • the combing result is determined by a combing distance between a combing envelope curve of the circular comb of the combing set, which is traveled by the combing set, and an upper nipper lip of a nipper unit.
  • To set the desired combing distance it is known that the base body together with the combing set can be changed in its position perpendicular to the shaft axis.
  • EP 3 754 055 A1 provides, for example, for an insert rail to be mounted between the base body and the shaft, whereby a distance between the insert rail and the base body can be changed by inserting a flat wedge.
  • EP 2 789 716 A1 a circular comb is known in which an exchangeable spacer element can be provided between a support element and the base body.
  • the circular comb according to the invention has a base body which carries a combing set on an outer, circular-arc-shaped outer section, and a mass balancing element which is designed for rotationally fixed fastening to the shaft on the side of the shaft opposite the combing set, as seen in the radial direction of the shaft.
  • the core of the invention consists in an adjustable support mechanism which is present between the base body and the mass balancing element when installed in the combing machine.
  • the support mechanism is designed in such a way that the base body and the mass balancing element contact each other directly in some areas and the base body and the mass balancing element are in their relative Position relative to each other can be changed perpendicular to the shaft axis, so that the position of the combing tips of the combing set can be adjusted.
  • the support mechanism combines the adjustable position of the combing tips with a stable support of the base body on the mass balancing element due to the direct contact. This improves the stability of the circular comb.
  • the base body is in direct contact, preferably in form-fitting contact, with a counterweight body of the mass balancing element. Additional support elements are not required.
  • the circular comb has a simple and stable structure. This increases the operational reliability of the combing machine. In particular, safe operation is guaranteed even at high working speeds of the combing machine.
  • the direct contact between the base body and the mass balancing element also has the advantage of simple and precise alignment of the base body and the combing elements arranged on it in relation to the shaft axis. Unintentional tilting or twisting of the combing assembly in relation to the shaft axis is reduced, and in particular avoided.
  • the support mechanism particularly simplifies the assembly of the circular comb on the shaft.
  • the base body can be easily removed, for example to clean and/or replace the combing equipment.
  • the combing set has in particular several combing bars arranged tangentially in the circumferential direction one behind the other, which in their entirety cover a combing circumferential angle segment and define a combing area of the circular comb.
  • the combing bars can, for example, be separately be received and fixed in corresponding comb receptacles of the base body, in particular be releasably fixed.
  • the base body of the circular comb can, for example, be a one-piece base body. It can also be made up of several parts.
  • the base body can, for example, have a grid structure in order to achieve a reduced weight while at the same time ensuring high stability.
  • the mass balancing element is attached to the shaft in a rotationally fixed manner.
  • the mass balancing element can be fixed to the shaft using fastening screws that are guided through the shaft.
  • the fastening screws are preferably screwed into a counterholder opposite the shaft. This ensures that the mass balancing element is securely fixed to the shaft in a rotationally fixed manner.
  • the mass balancing element can be clamped to the shaft using brackets that enclose the shaft.
  • the brackets can be pressed into corresponding receptacles in the mass balancing element, in particular a counterweight body of the mass balancing element, using pressure elements.
  • the location and direction information used refers in particular to the axis of rotation of the shaft, which is also referred to as the shaft axis.
  • the shaft axis defines a cylindrical coordinate system.
  • “axial” stands for an orientation in the direction of the shaft axis
  • “radial” for an orientation perpendicular to the shaft axis
  • "tangential” for an orientation in the circumferential direction around the shaft axis.
  • the combing direction of the circular comb is in particular the direction of rotation in which the circular comb rotates with the shaft around the shaft axis. It is in particular one of the two circumferential directions of the shaft axis.
  • Textile fibres here include in particular wool fibres, cotton fibres, synthetic fibres, chemical fibres or fibres consisting of a mixture of at least two of the above-mentioned fibre types.
  • a favorable embodiment is one in which the adjustable support mechanism is designed for a linear displacement, in particular a shift, of the base body relative to the mass balancing element.
  • the support mechanism is particularly preferably designed for a linear displacement, in particular a shift, of the base body relative to the mass balancing element in a direction oriented perpendicular to the shaft axis.
  • the base body can be displaceable, in particular displaceable, along a direction that runs radially to the shaft axis opposite the mass balancing element in relation to the shaft axis.
  • a linear displacement enables simple and effective adjustment of the positions of the combing tips, in particular of a combing envelope curve traveled by the combing tips.
  • the linear displacement, in particular the shift, of the base body relative to the mass balancing element is guided.
  • surface areas of the base body or the mass balancing element that are in direct contact can be shifted relative to one another during the linear displacement. This ensures a smooth and precise linear displacement in one direction while simultaneously determining the relative position in other spatial directions.
  • the adjustable support mechanism is designed to set a different relative position between the base body and the mass balancing element perpendicular to the shaft axis at a first axial end viewed in the direction of the shaft axis than at a second axial end viewed in the direction of the shaft axis.
  • the circular comb is particularly flexible and can be adapted precisely to the respective application, in particular to the respective combing machine.
  • a specified combing distance can be set precisely and easily over the entire length of the base comb in the direction of the shaft axis.
  • a favorable design is one in which the adjustable support mechanism is designed for a pivoting movement of the base body relative to the mass balancing element, in particular about a pivot axis running parallel to the shaft axis and laterally offset from the shaft axis.
  • a pivoting movement enables the relative position of the base body and mass balancing element to be adjusted easily and smoothly.
  • the pivot axis is advantageously arranged parallel to the shaft axis and laterally offset from it. This causes a particularly effective change in the distance of the comb tips to the shaft axis during pivoting.
  • the parallel course of the pivot axis to the shaft axis has the advantage that the change in the position of the comb tips relative to the shaft axis occurs evenly over the entire length of the circular comb in the direction of the shaft axis.
  • a favorable design is one in which the base body is supported exclusively on the mass balancing element when assembled. There is no direct connection between the base body and the shaft axis. This has the advantage that the base body only needs to be aligned with respect to the mass balancing element during assembly. Loosening of fastening elements between the base body and the shaft is avoided. Assembly is simple and not prone to errors.
  • the circular comb is structurally simple and durable.
  • a favorable design is one in which the mass balancing element has at least one contact surface for contacting the shaft when assembled.
  • the contact surface between the mass balancing element and the shaft leads to high stability.
  • the mass balancing element can be firmly and securely attached to the shaft. This does not affect the easy removal and installation of the base body.
  • a favorable design is one in which the base body has an inner section facing the shaft, the inner section defining a recess with an inner wall of the recess, with a free space being present between the inner wall of the recess of the base body and the shaft in the assembled state.
  • the free space defines a distance between the base body and the shaft. This ensures in a particularly simple manner that the base body is only supported on the mass balancing element.
  • the free space also reduces the weight of the circular comb, in particular the base body. This enables safe and efficient operation of the combing machine, especially at high working speeds.
  • the recess inner wall in particular has an inner wall radius which is defined as the smallest distance in the radial direction between the shaft axis and the recess inner wall.
  • the inner wall radius is, for example, between 124% and 250% of the shaft radius, in particular between 155% and 210% of the shaft radius.
  • the inner wall radius can be about 206%, about 177% or about 155% of the shaft radius.
  • Example shaft radii are 15 mm, 17.5 mm, 20 mm, 22.5 mm or 25 mm.
  • the inner wall radius in the assembled state can be selected to be, for example, about 31 mm or about 36 mm.
  • the clearance has in particular a clearance radius between the inner wall of the recess and a lateral surface of the shaft in the assembled state.
  • the clearance radius is defined as the smallest distance in the radial direction between the inner wall of the recess and the lateral surface of the shaft.
  • the clearance radius is, for example, between 24% and 150% of a shaft radius of the shaft of the combing machine, in particular between 55% and 110% of the shaft radius.
  • a design is advantageous in which the mass balancing element is at least partially accommodated in the recess in the assembled state.
  • the at least partial accommodation of the mass balancing element in the recess ensures a compact and stable design of the circular comb.
  • the mass balancing element can preferably contact a partial area of the inner wall of the recess in order to ensure secure and stable support of the base body.
  • a favorable design is one in which the base body as part of the support mechanism has at least two parallel to the shaft axis Has fixing surfaces, wherein the base body in the assembled state makes direct, positive contact with the mass balancing element in the area of the fixing surfaces, so that the base body with the combing set mounted on it is aligned and fixed in the direction of the shaft axis.
  • the base body is particularly preferably aligned parallel to the shaft axis due to the direct contact of the mass balancing element in the area of the fixing surfaces.
  • the at least two fixing surfaces ensure stable and secure support of the base body on the mass balancing element. Unintentional tilting or pivoting of the base body relative to the mass balancing element, in particular in the circumferential direction, is avoided. This makes assembly simple and less prone to errors.
  • the fixing surfaces can, for example, rest against corresponding counter-fixing surfaces of the mass balancing element, in particular a counterweight body of the mass balancing element, in particular in a flat manner.
  • the fixing surfaces and counter-fixing surfaces can in particular be displaceable relative to one another in certain areas in order to enable a guided displacement of the base body relative to the mass balancing element.
  • a design in which the at least two fixing surfaces are flat is advantageous.
  • the flat fixing surfaces simplify a linear displacement, in particular a shift, of the base body relative to the mass balancing element in order to adjust the position of the combing tips.
  • a large-area contact between the base body and the mass balancing element is ensured, so that the support of the base body on the mass balancing element is particularly stable.
  • a design of the circular comb is advantageous in which the at least two fixing surfaces are curved in a plane defined perpendicular to the shaft axis, in particular they are curved differently.
  • the curved course of the at least two fixing surfaces enables the base body to be pivoted easily and in a guided manner relative to the mass balancing element.
  • a positive contact between the base body and the mass balancing element is not impaired by the pivotability.
  • the mass balancing element particularly preferably has correspondingly curved counter-fixing surfaces in order to ensure direct surface contact, in particular regardless of the pivot position.
  • a different curvature of the at least two fixing surfaces in the plane defined perpendicular to the shaft axis also has the advantage that mounting the base body in an unintended orientation is avoided. This makes installation easier and increases operational reliability.
  • a design of the circular comb is advantageous in which the at least two fixing surfaces have the same axis center in the plane defined perpendicular to the shaft axis.
  • the common axis center can in particular define a pivot axis for a relative pivoting movement between the base body and the mass balancing element. This enables the base body to pivot particularly smoothly and precisely relative to the mass balancing element.
  • the common axis center is preferably offset laterally relative to the shaft axis in the plane defined perpendicular to the shaft axis. This enables the position of the comb tips to be adjusted particularly easily and effectively by pivoting the base body relative to the mass balancing element.
  • the support mechanism has detachable fastening means for clamping the variable position between the base body and the mass balancing element.
  • the detachable fastening means can be formed by clamping screws, which can be screwed into corresponding holes in the mass balancing element.
  • the detachable fastening means, in particular the clamping screws are guided in the assembled state through receptacles formed in the base body, in particular elongated holes.
  • the detachable fastening means can be guided through corresponding receptacles, in particular elongated holes, in the area of fixing surfaces of the base body. The clamping force is then brought about in the area of the fixing surfaces.
  • Elongated holes enable simple, in particular guided, positioning of the base body relative to the mass balancing element when the fastening means are released. With the help of the elongated holes, a relative position between the base body and the mass balancing element can be flexibly adjusted.
  • the detachable fastening means in particular the clamping screws, are aligned in such a way that a clamping force is oblique, preferably substantially perpendicular, to an adjustment direction in which the relative position of the base body to the mass balancing element is adjusted.
  • a clamping force is oblique, preferably substantially perpendicular, to an adjustment direction in which the relative position of the base body to the mass balancing element is adjusted.
  • the support mechanism is precisely adjustable.
  • a favorable design of the circular comb is one in which the support mechanism has orientation means that ensure a relative target orientation of the base body and the mass balancing element in the assembled state. This reliably prevents assembly in the wrong orientation.
  • the orientation means can be provided by at least two fixing surfaces that run with different curvatures in a plane defined perpendicular to the shaft axis.
  • the orientation means can also have detachable fastening means that are arranged on different sides of the base body and the mass balancing element offset from one another, in particular offset from one another in the direction of the shaft axis, in relation to the circumferential direction.
  • a favorable design of the circular comb is one in which the support mechanism has a suspension means on the base body and a counter suspension means on the mass balancing element in order to suspend the base body on the mass balancing element during assembly. This simplifies assembly. It is not necessary to hold the base body by hand during assembly. This also increases the precision of setting the position of the comb tips. Suspension means and counter suspension means in the form of a bayonet slot or a bayonet projection have proven to be particularly suitable. This enables the base body to be suspended on the mass balancing element easily and without tools. Preferably, a relative position between the base body and the mass balancing element can be at least roughly specified by the bayonet lock formed in this way. This facilitates assembly.
  • a particularly favorable design is one in which the suspension means on the base body and the counter suspension means on the mass balancing element are involved in the variable relative positioning of the base body and the mass balancing element to one another.
  • the suspension means can be dimensioned such that the counter suspension means are held therein without play.
  • bayonet slots can have a dimension so that bayonet projections are held therein without play.
  • bayonet projections can be formed, for example, as part of an eccentric shaft.
  • the position of the bayonet projections can be changed by rotating the eccentric shaft. It is particularly preferred to arrange an eccentric shaft with bayonet projections at each of the axial ends of the circular comb. An arrangement of the eccentric shafts in or on the mass balancing element has proven to be particularly suitable.
  • a particularly preferred embodiment allows a simple application of force to adjust the suspension means and/or the counter-suspension means.
  • the eccentric shaft can be rotated by applying force using an eccentric adjustment screw.
  • An eccentric adjustment screw can, for example, be attached to an actuating surface the eccentric shaft offset from an eccentric shaft central longitudinal axis. It is particularly advantageous if the eccentric shaft is preloaded against the force applied by the eccentric adjustment screw. This ensures that the eccentric shaft can be easily reset when the eccentric adjustment screw is turned back.
  • a rotation angle range of the eccentric shaft can be limited by a limiting element. This prevents the eccentric shaft from twisting and thus a change in the relative position of the mass balancing element to the base body beyond a specified adjustment range.
  • a fixed limiting element can protrude into a limiting holder provided in the eccentric shaft. The maximum angle of rotation is then defined by stop surfaces of the limiting holder that are opposite one another in the circumferential direction of the eccentric shaft.
  • a favorable design is one in which the support mechanism has adjustment means for adjusting the variable relative position between the base body and the mass balancing element. This enables particularly simple and precise adjustment of the relative position of the base body and the mass balancing element. It is not necessary to hold the base body by hand while adjusting the relative position.
  • the circular comb is easy to install and reliable in operation. It is particularly preferred if appropriate adjustment means are present in the area of the respective axial ends of the circular comb.
  • Suitable adjustment means can be formed, for example, by adjustable suspension means and/or counter-suspension means, as described above.
  • Particularly suitable suspension means can, for example, be the bayonet projections described above arranged on an eccentric shaft, particularly preferably in conjunction with corresponding eccentric adjustment means.
  • the adjustment means can also have adjustment screws.
  • the adjustment screws can, for example, be screwed into the base body or the mass balancing element and rest on the other component.
  • an adjustment screw can be provided at each of the axial ends of the circular comb.
  • the adjustment screw is easily accessible and operable at the axial ends.
  • an adjustment screw can be screwed into the mass balancing element and rest on the base body, in particular on a front cover of the base body. This ensures that sufficient force is applied to adjust the position.
  • the adjustment means do not require a permanent application of force, since the relative position of the base body to the mass balancing element is preferably fixed using detachable fastening means.
  • Fig. 1 is a schematic representation of a combing machine with a circular comb mounted on a shaft, comprising a base body and a mass balancing element
  • Fig. 2 is a side view of an embodiment of the
  • Circular comb for the combing machine according to Fig. 1 Circular comb for the combing machine according to Fig. 1,
  • Fig. 3 is a front view of the circular comb mounted on the shaft according to Fig. 2, with an end cover not shown,
  • Fig. 4 is a perspective view of the main body of the
  • Fig. 5 is a perspective view of the mass balancing element of the circular comb according to Fig. 2,
  • Fig. 6 a plan view of the mass balancing element according to
  • Fig. 7 is a perspective view of an eccentric shaft for
  • Fig. 8 is a longitudinal section A-A through the mass balancing element according to Fig. 6,
  • Fig. 9 a longitudinal section B-B through the mass balancing element according to Fig. 6,
  • Fig. 10 a longitudinal section CC through the mass balancing element according to Fig. 6,
  • Fig. 11 is a front view of another embodiment of a mass balancing element for a circular comb,
  • Fig. 12 is a side view of the mass balancing element according to Fig. 11,
  • Fig. 13 is a partially sectioned plan view of the mass balancing element according to Fig. 11, with section planes sl and s2 indicated in Fig. 12,
  • Fig. 14 is a side view of another embodiment of a circular comb
  • Fig. 15 is a side view of another embodiment of a circular comb
  • Fig. 16 is a side view of another embodiment of a circular comb
  • Fig. 17 is a front view of another embodiment of a circular comb
  • Fig. 18 is a partially sectioned front view of another embodiment of a circular comb
  • Fig. 19 shows a section of a combing machine with a further embodiment of a partially sectioned circular comb, which is designed for pivoting displacement of the base body relative to the mass balancing element,
  • Fig. 20 is a front view of the base body of the circular comb according to Fig. 19,
  • Fig. 21 a perspective view of the base body according to
  • Fig. 22 is a front view of another embodiment of a circular comb designed for pivotable displacement of the base body relative to the mass balancing element.
  • Fig. 1 shows an embodiment of a combing machine 1 for combing textile fibers.
  • the combing machine is only shown schematically in Fig. 1. It has a nipper unit 2, a take-off unit 3, a brush 4 and a circular comb 6 mounted on a shaft 5.
  • the nipper unit 2 is used to feed the textile fibers to be combed. It has an upper nipper 7 and a lower nipper 8.
  • the nipper unit 2 carries out a relative movement in relation to the other machine components of the combing machine 1, in particular in relation to the take-off unit 3 and its fixed take-off rollers 9, 10, 11 and 12. The relative movement is brought about by means of a gear by rotation around a nipper shaft 13.
  • the take-off rollers 9, 10, 11 and 12 of the take-off unit 3 are arranged in pairs. They serve to collect and remove the textile fibers after combing.
  • the circular comb 6 is intended for combing the textile fibers.
  • An upper nipper lip 14 is formed on an end of the upper nipper 7 facing the circular comb 6.
  • the upper nipper lip 14 works together with the circular comb 6 to comb the textile fibers.
  • a fixed comb (not shown) attached to the fixed comb holder 52 of the nipper unit 2 can also be present.
  • the circular comb 6 is only shown schematically in Fig. 1. It has a base body 15 and a mass balancing element 16.
  • the mass balancing element 16 is attached to the shaft 5 in a rotationally fixed manner.
  • the base body 15 is supported on the mass balancing element 16.
  • a combing set 17 is arranged along a circular arc-shaped outer section of the base body 15.
  • the combing set 17 has several combing bars 18 arranged in the circumferential direction of the base body 15 around a shaft axis W of the shaft 5.
  • the combing set 17 has six combing bars 18.
  • the combing bars 18 cover in their entirety a combing circumferential angle segment which defines a combing range of the circular comb 6.
  • the combing circumferential range can be, for example, between 75 ° and 150 °.
  • the shaft 5 When the combing machine 1 is operating, the shaft 5 is driven to rotate about the shaft axis W, in particular at a discontinuous angular speed. This causes the circular comb 6 to rotate via the mass balancing element 16 which is fixedly attached to the shaft 5.
  • the combing machine 1 is operated with a high number of comb cycles of, for example, 600 revolutions per minute of the shaft 5 and thus of the circular comb 6.
  • the shaft axis W runs in the longitudinal direction of the circular comb 6.
  • the shaft axis W can in particular also be understood as the central longitudinal axis of the circular comb 6.
  • a cylindrical coordinate system is defined with an axial direction z oriented along the shaft axis W, with a radial direction r oriented in the distance direction to the shaft axis W and with a tangential direction cp pointing in the circumferential direction around the shaft axis W.
  • a plane is defined perpendicular to the shaft axis W, which corresponds to the drawing plane in Fig. 1 and is also referred to below as the normal plane N.
  • the normal plane N is spanned in the cylindrical coordinates by the radial direction r and the circumferential direction cp.
  • the combing envelope curve 19 is circular in the normal plane N and has a combing radius R which corresponds to the maximum radial distance of combing tips 33 of the combing set 17 from the shaft axis W.
  • R The distance between the upper nipper lip 14 and the combing assembly 17, in particular its combing tips 33, is referred to as the combing distance d.
  • the correct positioning of the combing tips 33 of the combing assembly 17 to the upper nipper lip 14 and thus the combing distance d are important parameters for the operation of the combing machine 1.
  • the position of the combing tips 33 of the combing assembly 17 is adjustable.
  • a relative position of the base body 15 to the mass balancing element 16 perpendicular to the shaft axis W can be changed.
  • the relative position can be adjusted in such a way that a maximum radial distance of the combing tips 33 from the shaft axis W and thus of the combing radius R can be changed.
  • the mass balancing element 16 has a counterweight body 20. Brackets 22 are attached to the counterweight body 20 by means of pressure pieces 21. In the assembled state, the shaft 5 is clamped between the brackets 22 and the mass balancing element 16, so that the mass balancing element 16 is attached to the shaft 5 in a rotationally fixed manner. In addition to or as an alternative to the brackets 22, the mass balancing element 16, in particular its counterweight body 20, can be screwed to the shaft.
  • a recess 50 with an arcuate cross-section is formed in the counterweight body 20 for partially receiving the shaft.
  • the recess 50 forms a contact surface 51 of the mass balancing element 16 for direct contact with the shaft 5 in the assembled state.
  • the base body 15 has comb receptacles 23 in which the comb bars 18 can be received and locked in a known manner.
  • the base body 15 is not designed to be full-volume, but has a grid structure made of grid struts 24. The grid structure ensures that the base body 15 is rigid and lightweight at the same time.
  • the assembled state of the circular comb 6 has front covers 25 which are held in corresponding receptacles 27 of the base body 15 by screws 26.
  • the base body 15 has an arcuate cross-section in the normal plane N perpendicular to the shaft axis W.
  • An inner section of the base body 15 facing the shaft 5 in the assembled state defines a recess 28 with an inner recess wall 29.
  • a free space is formed between the shaft 5 and the inner recess wall 29.
  • the free space has a free space radius F.
  • the free space radius F is defined as the smallest distance in the radial direction between the inner recess wall 29 and a lateral surface of the shaft 5.
  • the shaft 5, the brackets 22 and at least partially the mass balancing element 16 are accommodated in the recess 28 in the assembled state.
  • the base body 15 is not in direct contact with the shaft 5 in the assembled state, in particular the base body is not directly connected to the shaft 5 or attached to it.
  • the base body 15 is supported exclusively on the mass balancing element 16.
  • a support mechanism 30 is formed between the base body 15 and the mass balancing element 16, which is described in detail below.
  • the support mechanism 30 has a direct positive contact between the base body 15 and the mass balancing element 16.
  • the base body 15 has two fixing surfaces 31 extending parallel along the shaft axis W.
  • the fixing surfaces 31 are flat and part of the recess inner wall 29. In the assembled state, the fixing surfaces 31 lie in a positive fit on flat counter-fixing surfaces 32 of the mass balancing element 16, which run parallel to the shaft axis W.
  • the counter-fixing surfaces 32 are designed as lateral surfaces of the counterweight body 20. Due to the positive contact of the fixing surfaces 31 with the counter-fixing surfaces 32, the base body 15 with the combing set 17 mounted on it is aligned and fixed in the direction of the shaft axis W in the assembled state.
  • a twisting of the base body 15 relative to the mass balancing element 16 in the direction perpendicular to the flat fixing surfaces 31 is avoided.
  • the flat design of the fixing surfaces 31 and the counter-fixing surfaces 32 allows a linear displacement of the base body 15 relative to the mass balancing element 16 in order to change their relative position and to adjust the position of the combing tips 33.
  • the base body 15 can be linearly displaced relative to the mass balancing element 16 perpendicular to the shaft axis W. The displacement takes place in a direction perpendicular to the shaft axis W and perpendicular to a surface normal of the fixing surfaces 31.
  • the base body 15 and the mass balancing element 16 are clamped together using detachable fastening means in the form of clamping screws 34.
  • the clamping screws 34 are guided through elongated holes 35 formed in the base body 15 and screwed into holes in the counterweight body 20 of the mass balancing element 16.
  • the clamping screws 34 clamp the base body 15 to the mass balancing element 16 using the fixing surfaces 31 or counter fixing surfaces 32.
  • the resulting clamping force acts in the direction of the surface normal of the fixing surfaces 31 or counter fixing surfaces 32. This means that the clamping force is applied over a large area.
  • the clamping force acts perpendicular to a direction of displacement of the base body 15 relative to the mass balancing element 16. A linear displacement and thus the adjustment of the position of the combing tips 33 can thus be precisely adjusted and is not affected by the clamping force.
  • Bores in the counterweight body 20 for screwing in the clamping screws 34 and the corresponding elongated holes 35 of the base body 15 are arranged in pairs opposite each other in the circumferential direction cp.
  • the opposing bores and elongated holes 35 are at the same axial position in the direction of the z-direction or the shaft axis W.
  • the opposing clamping screws and elongated holes can also have an offset, in particular an offset in the direction of the shaft axis W. This breaks the symmetry of the detachable fastening means.
  • the base body and mass balancing element can only be connected to each other in a predetermined relative orientation.
  • This symmetry break represents an orientation means that ensures a relative target orientation of the base body and the mass balancing element in the assembled state.
  • Other orientation means, in particular symmetry breaks, are also conceivable.
  • the flat fixing surfaces and counter-fixing surfaces opposite each other in the normal plane N cannot run parallel to each other, so that only one fixing surface is suitable for form-fitting contact with one of the counter-fixing surfaces.
  • the design of the elongated holes 35 allows a change in the relative position of the base body 15 to the mass balancing element 16.
  • the clamping screws 34 can be loosened and the base body 15 can be brought into the desired position relative to the mass balancing element 16. In the desired relative position, the clamping screws 34 can be tightened again to clamp the base body 15 to the mass balancing element 16.
  • the linear displacement of the base body 15 relative to the mass balancing element 16 and thus relative to the shaft 5 can be carried out manually by lifting the base body 15 into the corresponding position with the clamping screws 34 loosened.
  • the base body 15 can be pressed manually against a gauge band inserted between the combing tips 33 and the upper nipper lip 14.
  • the support mechanism 30 of the round comb 6 adjustment means 36 for adjusting the variable relative position between the base body 15 and the mass balancing element 16.
  • the adjustment means 36 have eccentric shafts 37 inserted into the counterweight body 20 of the mass balancing element 16.
  • the adjustment means 36 have two eccentric shafts 37, which are assigned to the respective end faces of the mass balancing element 16.
  • the eccentric shafts 37 are inserted into the counterweight body 20 in such a way that an eccentric shaft central longitudinal axis E runs perpendicular to the shaft axis W and perpendicular to the counter-fixing surfaces 32.
  • the eccentric shaft central longitudinal axis E runs in a width direction of the mass balancing element 16.
  • Each eccentric shaft 37 has bayonet projections 38 arranged at its respective ends eccentrically to the eccentric shaft central longitudinal axis E.
  • the bayonet projections 38 lying opposite one another each have the same offset to the eccentric shaft central longitudinal axis E.
  • the bayonet projections 38 are guided laterally of the counterweight body 20 through through openings 39 in the counter-fixing surfaces 32 and protrude laterally beyond them.
  • the bayonet projections 38 cooperate with bayonet slots 40 in the base body 15.
  • the bayonet projections 38 and the bayonet slots 40 form a bayonet lock, via which the base body 15 can be suspended from the mass balancing element 16.
  • the bayonet slots 40 act as a suspension means and the bayonet projections 38 as a counter-suspension means of the support mechanism 30. This simplifies assembly. Holding the base body by hand is not necessary even when the clamping screws 34 are unscrewed.
  • the displacement of the bayonet projections 38 has a component parallel to the shaft axis W and a component perpendicular to the shaft axis W.
  • the movement component perpendicular to the shaft axis is relevant for setting the relative position of the base body 15 to the mass balancing element 16.
  • the bayonet slots are therefore dimensioned in the direction perpendicular to the shaft axis so that the bayonet projections 38 are held in the bayonet slots 40 without play in this direction.
  • the movement component parallel to the shaft axis W is compensated by a corresponding longitudinal extension of the bayonet slots 40.
  • the eccentric shaft 37 When the eccentric shaft 37 rotates, the movement component perpendicular to the shaft axis W of the bayonet projections 38 is transferred to the base body 15 via the bayonet slots 40.
  • the bayonet projections 18 and the bayonet slots 40 and thus the corresponding suspension means or counter-suspension means of the support mechanism 30 are involved in the variable relative positioning of the base body 15 and its mass balancing element 16 to one another.
  • the corresponding eccentric arrangement of the bayonet projections 38 at the opposite ends of the eccentric shaft 37 also ensures that the sides of the base body 15 that are opposite one another in the circumferential direction cp are evenly displaced relative to the mass balancing element 16. Wedging and/or tilting of the base body 15 is thus reliably avoided.
  • the eccentric shaft 37 has two grooves arranged on the casing side and offset in the eccentric shaft center longitudinal direction E, the bottom of which forms an actuating surface 41 and a counter-actuating surface 42.
  • An eccentric adjusting screw 43 engages the actuating surface 41 on one side of the eccentric shaft central longitudinal axis E. By screwing in the eccentric adjusting screw 43, the actuating surface 41 is subjected to an adjusting force. Due to the one-sided application of force, screwing in the eccentric adjusting screw 43 causes the eccentric shaft 37 to twist.
  • the eccentric adjustment screws 43 of the respective eccentric shafts 37 protrude from the front of the mass balancing element 16.
  • the eccentric adjustment screws 43 are easily accessible and can be actuated to cause rotation of the eccentric shaft 37.
  • the eccentric adjustment screws 43 are each secured against unintentional actuation by a locking nut 44.
  • the counter-actuating surface 42 is subjected to a counterforce by a pressure piece 45 on one side of the eccentric shaft central longitudinal axis E.
  • the pressure piece 45 is pre-tensioned against the counter-actuating surface 42 by means of a compression spring 46.
  • the compression spring 46 is supported on a threaded bolt 47. The pre-tension and thus the counterforce can be adjusted by screwing the threaded bolt 47 in or out.
  • the actuating surface 41 and the counter-actuating surface 42 are parallel to one another.
  • the eccentric adjusting screw 43 and the pressure piece 45 act on opposite sides of the actuating surface 41 and the counter-actuating surface 42, respectively, in relation to the eccentric shaft central longitudinal axis E.
  • the counterforce caused by the pressure piece 45 therefore counteracts an adjustment force caused by the eccentric adjusting screw.
  • the counterforce therefore causes the eccentric shaft to rotate in the opposite direction to the direction of rotation caused by screwing in the eccentric adjusting screw 43.
  • the counterforce must be overcome in order to rotate the eccentric shaft.
  • the counterforce causes the eccentric shaft 37 to rotate back.
  • a limiting recess is also formed with limiting stops 48 located opposite one another in the circumferential direction of the eccentric shaft 37.
  • a limiting element in the form of a limiting screw 49 engages in the limiting recess between the limiting stops 48.
  • the limiting stops 48 interact with the limiting screw 49 to define a maximum angle of rotation a of the eccentric shaft 37.
  • the adjustment means 36 allow the relative position of the base body 15 and the mass balancing element 16 to be set easily and precisely by operating the eccentric adjustment screws 43. After setting the desired relative position, this can be fixed by tightening the clamping screws 34.
  • the adjustment means 36 can be adjusted independently of one another at the opposite axial ends of the circular comb defined in the direction of the shaft axis W.
  • the adjustable support mechanism 30 is therefore designed to be mounted on a support in the direction of the A different relative position between the base body 15 and the mass balancing element 16 perpendicular to the shaft axis W can be set at the axial first end, as seen from the shaft axis W, than at an axial second end opposite the axial first end in the direction of the shaft axis W. This allows a provided meshing distance d to be set precisely and accurately, regardless of a possible longitudinal tilting of the upper nipper lip 14.
  • the meshing radius R can vary along the shaft axis W.
  • mass balancing element 116 can, for example, be combined with the base body 15 of the previous embodiment to form a circular comb.
  • the mass balancing element 116 has a counterweight body 120.
  • the counterweight body 120 is essentially the same as the counterweight body 20 of the mass balancing element 16 according to the previous embodiment. Differences are that the limit screw 49 for limiting the rotation of the eccentric shaft is screwed in at the front, as can be seen in particular from the partially sectioned illustration in Fig. 13.
  • the partial sections correspond to section planes sl and s2 shown in Fig. 12.
  • the section plane sl is at the level of the limit screws 49
  • the section plane s2 is at the level of spring pressure pieces 61 with external thread.
  • the spring pressure pieces 61 are each screwed into a corresponding bore 62 in order to counteract an adjustment force of the respective adjustment screws 43.
  • fastening screws 63 are passed from below through the counterweight body 120 and corresponding holes in the shaft.
  • the fastening screws 63 are designed as cylinder screws.
  • the fastening screws 63 are screwed into a counterholder 64.
  • the counterholder 64 extends parallel to the shaft axis and, in the assembled state, is arranged opposite the mass balancing element 116 in relation to the shaft.
  • the counterholder 64 is connected to the mass balancing element 116 via the fastening screws 63.
  • FIG 14 shows a further embodiment of a circular comb 206.
  • the circular comb 206 corresponds in the design of the base body 15 and the mass balancing element 16 to the circular comb 6 previously described with reference to Figures 2 to 10.
  • the circular comb 206 differs from the circular comb 6 only in terms of the design of the support mechanism 230.
  • the support mechanism 230 of the circular comb 206 has the eccentric shafts 37, but no eccentric adjustment screws and pressure pieces that counteract them.
  • the eccentric shaft 37 runs freely in the support mechanism 230 except for a limit of the angle of rotation.
  • the base body 15 can be raised. Depending on the raise, the eccentric shaft 37 is rotated in order to bring the bayonet projections into the appropriate position.
  • the eccentric shaft 37 and the bayonet projections 38 arranged thereon are therefore only involved in the adjustment of the relative position insofar as they provide additional guidance for the base body 15.
  • the base body 15 can be hooked into the counter-hook means formed by the bayonet projections 38 for assembly using the hooking means designed as bayonet slots 40.
  • a further embodiment of a circular comb 306 is described.
  • the circular comb 306 differs from the previously described circular comb 206 in the design of the support mechanism 330.
  • the bayonet slots 340 serving as the means for hanging the base body 315 are dimensioned such that the bayonet projections 338 are accommodated therein with play.
  • the bayonet projections 338 therefore do not have to be mounted on a corresponding eccentric shaft, but can, for example, be formed directly onto the counter-fixing surfaces 332. This simplifies the structure of the support mechanism. To move the base body linearly relative to the mass balancing element, the base body can be lifted into the correct position with the clamping screws loosened.
  • the bayonet projections 338 can also be attached to a rotatably mounted eccentric shaft in order to ensure sufficient relative positioning regardless of a width of the bayonet slots 340.
  • the circular comb 406 differs from the previously described circular combs in that the support mechanism 430 has no suspension means on the base body 415 and no counter-suspension means on the mass balancing element 416 for suspending the base body 415 during assembly.
  • the base body 415 is held manually and moved into the desired target position relative to the mass balancing element 416.
  • the clamping screws 34 are screwed through the elongated holes into the mass balancing element 416 to produce a clamping fixation of the base body 415.
  • a further embodiment of a circular comb 506 is described with reference to Figure 17.
  • the circular comb 506 has a support mechanism 530 with adjustment means 536 for adjusting the position between the mass balancing element 516 and the base body 515.
  • the adjustment means 536 each comprise an adjustment screw 65 which is guided through a corresponding hole in the counterweight body 520 in the area of the axial ends of the mass balancing element 516 and screwed into it.
  • the screws 65 can be actuated from an underside of the counterweight body 520 opposite the shaft 5.
  • a screw tip 66 of the screw 65 is supported on a stop edge 67 of the front cover 25.
  • the cover 25 and the base body 515 attached to it can be raised or lowered by screwing in or unscrewing the adjustment screw 65.
  • the adjusting screws 65 are a structurally simple and effective adjusting means 536. For clamping fixation, the clamping screws 34 are tightened after the desired relative position has been reached.
  • the circular comb 506 can correspond in other respects to the circular combs described above.
  • the adjusting screws 65 can be combined in particular with the previously described embodiments of the circular combs, in particular with the circular combs 206, 306 and 406 shown in Figures 14 to 16. With reference to Figure 18, a further embodiment of a circular comb 606 is described.
  • the support mechanism 630 of the circular comb 606 has adjustment means 636 in the form of adjustment screws 665.
  • the adjustment screws 665 are screwed into a corresponding hole in the mass balancing element 616 at the respective axial ends from above.
  • a screw head 68 of the adjustment screw 665 rests on the support edge 67 of the respective front cover 25. The screw head 68 can be reached and actuated from the front. By screwing in or unscrewing the screw 665, the cover 25 and thus the base body 615 can be lowered or raised in relation to the mass balancing element 616.
  • the adjustment means have only one adjustment screw arranged at one of the axial ends.
  • at least one adjustment screw which can be actuated in particular from an underside of the mass balancing element, can be arranged at any position along the shaft axis.
  • the at least one adjustment screw can be supported on at least one corresponding support edge of the base body, which can be formed, for example, on an inner wall of a recess.
  • a support mechanism 730 of the circular comb is designed for a pivoting movement of the base body 715 against above the mass balancing element 716.
  • a joint extension 70 is arranged on a counterweight body 720 of the mass balancing element 716.
  • the joint extension 70 has an essentially circular cross-section in a plane perpendicular to the shaft axis W, which ends in a connecting web 71 connecting the joint extension 70 to the counterweight body 720.
  • the joint extension 70 runs parallel to the shaft axis W with a constant cross-section.
  • a joint receptacle 72 extending along the shaft axis W is formed in the base body 715.
  • An inner contour of the joint receptacle 72 corresponds to an outer contour of the joint extension 70.
  • the joint extension 70 is held in the joint receptacle 72.
  • the joint extension 70 and the joint receptacle form a pivot joint. This defines a pivot axis S which runs parallel to, but laterally offset from, its shaft axis W.
  • An inner surface of the joint receptacle 72 forms a first fixing surface of the base body 715, which in the assembled state is in positive contact with an outer surface of the articular extension 70.
  • a second fixing surface 74 is formed in an area of a recess inner wall 729 opposite the shaft axis W.
  • the fixing surfaces 73, 74 run parallel to the shaft axis W. In the normal plane N defined perpendicular to the shaft axis W, the fixing surfaces 73, 74 run curved.
  • the fixing surfaces 73, 74 have different radii of curvature.
  • the fixing surfaces 73, 74 have the same axis center, which corresponds to the position of the pivot axis S in the normal plane N defined perpendicular to the shaft axis W.
  • the fixing surfaces 73, 74 are therefore bent in a circular arc around the pivot axis S at least in sections. This ensures smooth and guided pivoting around the pivot axis S.
  • the second fixing surface 74 is in positive contact with a correspondingly curved counter-fixing surface 75 of the mass balancing element 716.
  • the base body 715 has elongated holes 35 for passing through the clamping screws 34.
  • the clamping screws 34 are screwed into holes 69 of the mass balancing element 716 to produce a clamping fixation of the base body 715 to the mass balancing element 716.
  • the clamping screws 34 can be loosened, which then enables pivoting about the pivot axis S.
  • the position of the combing tips 33 changes.
  • the combing radius R can be changed in this way to adjust the combing distance d.
  • the clamping screws 34 can be tightened to clamp the base body 715 relative to the mass balancing element 716.
  • the front covers 725 are designed to match the design of the base body 715, in particular in the area of the joint receptacle 72.
  • the opposite sides of the base body 715 and the mass balancing element 716 in the normal plane N are designed differently, in particular by forming the differently curved fixing surfaces 73, 74 or the counter fixing surface 75 and the outer contour of the articular process 70. This ensures that the base body 715 can only be mounted on the mass balancing element 716 in a certain predetermined orientation.
  • the differently curved fixing surfaces 73, 74 act as orientation means to ensure a desired orientation of the base body 715 and the mass balancing element 716.
  • a further embodiment of a circular comb 806 is explained with reference to Figure 22.
  • the circular comb 806 essentially corresponds to the circular comb 706 described with reference to Figures 19 to 21, in particular in the design of the base body 715.
  • the circular comb 806 differs only in the design of the support mechanism 830.
  • the support mechanism 830 has adjustment means 836 for adjusting the variable relative position between the base body 715 and the mass balancing element 816.
  • an adjustment screw 865 is screwed into the mass balancing element 816.
  • a screw head 868 of the adjustment screw 865 is supported on a support edge 867 of the front cover 725.
  • the screw head 868 can be operated on the front side to screw in or unscrew the adjusting screw 865.
  • the base body 715 By screwing in or unscrewing the adjusting screw 865 into the mass balancing element 816, the base body 715 is raised or lowered in the area of the screw head 868, which causes it to pivot about the pivot axis S. To achieve a secure support effect, the support edge 867 is curved in accordance with the pivoting movement.

Landscapes

  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Preliminary Treatment Of Fibers (AREA)

Abstract

L'invention concerne un peigne circulaire (6) conçu pour une peigneuse destinée à peigner des fibres textiles et à être fixée à un arbre de la peigneuse pouvant tourner autour d'un axe d'arbre (W). Ce peigne circulaire (6) comporte un corps de base (15) portant une garniture de peignage (17) et un élément de compensation de masse (16) destiné à être fixé solidaire en rotation sur l'arbre, sur le côté de l'arbre opposé à la garniture de peignage (17). Dans un état monté dans la peigneuse, un mécanisme d'appui (30) réglable est présent entre le corps de base (15) et l'élément de compensation de masse (16), le corps de base (15) et l'élément de compensation de masse (16) étant en contact direct l'un avec l'autre par endroits, et le corps de base (15) et l'élément de compensation de masse (16) pouvant être modifiés dans leur position relative l'un par rapport à l'autre perpendiculairement à l'axe de l'arbre (W), de sorte que la position de pointes de peignage (33) de la garniture de peignage (17) puisse être réglée.
PCT/EP2023/076977 2022-10-05 2023-09-28 Peigne circulaire pour peigneuse WO2024074407A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102022210530.3 2022-10-05
DE102022210530.3A DE102022210530A1 (de) 2022-10-05 2022-10-05 Rundkamm für eine Kämmmaschine

Publications (1)

Publication Number Publication Date
WO2024074407A1 true WO2024074407A1 (fr) 2024-04-11

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Application Number Title Priority Date Filing Date
PCT/EP2023/076977 WO2024074407A1 (fr) 2022-10-05 2023-09-28 Peigne circulaire pour peigneuse

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DE (1) DE102022210530A1 (fr)
WO (1) WO2024074407A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102022210530A1 (de) 2022-10-05 2024-04-11 Staedtler + Uhl Kg Rundkamm für eine Kämmmaschine

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE389608C (de) * 1922-10-31 1924-02-08 Hermann Heinrich Kaemmtrommel fuer Kaemmaschinen
EP2789716A1 (fr) 2013-04-12 2014-10-15 Maschinenfabrik Rieter Ag Peigne rond d'une peigneuse
WO2015166085A2 (fr) * 2014-05-02 2015-11-05 Staedtler + Uhl Kg Peigne circulaire et ensemble formant peigne circulaire muni d'un peigne circulaire fixé à un arbre
WO2018141532A1 (fr) * 2017-02-02 2018-08-09 Staedtler + Uhl Kg Peigne circulaire comprenant un segment de peignage et segment d'alignement
EP3754055A1 (fr) 2019-06-17 2020-12-23 Graf + Cie AG Peigne circulaire pour une peigneuse
DE102022210530A1 (de) 2022-10-05 2024-04-11 Staedtler + Uhl Kg Rundkamm für eine Kämmmaschine

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10163663A1 (de) 2001-12-21 2003-07-03 Rieter Ag Maschf Rundkamm für eine Kämmaschine
EP2426239B1 (fr) 2010-09-04 2013-03-06 Maschinenfabrik Rieter AG Peigne rond d'une peigneuse
CH715430A1 (de) 2018-10-04 2020-04-15 Graf Cie Ag Rundkamm für eine Kämmmaschine.

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE389608C (de) * 1922-10-31 1924-02-08 Hermann Heinrich Kaemmtrommel fuer Kaemmaschinen
EP2789716A1 (fr) 2013-04-12 2014-10-15 Maschinenfabrik Rieter Ag Peigne rond d'une peigneuse
WO2015166085A2 (fr) * 2014-05-02 2015-11-05 Staedtler + Uhl Kg Peigne circulaire et ensemble formant peigne circulaire muni d'un peigne circulaire fixé à un arbre
WO2018141532A1 (fr) * 2017-02-02 2018-08-09 Staedtler + Uhl Kg Peigne circulaire comprenant un segment de peignage et segment d'alignement
EP3754055A1 (fr) 2019-06-17 2020-12-23 Graf + Cie AG Peigne circulaire pour une peigneuse
DE102022210530A1 (de) 2022-10-05 2024-04-11 Staedtler + Uhl Kg Rundkamm für eine Kämmmaschine

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