阅读说明：本技术 用于梳棉机的滚筒 (Roller for carding machine ) 是由 E.梅德韦茨基 于 2018-05-16 设计创作，主要内容包括：本发明涉及一种用于梳棉机(1)的滚筒(5),其包括具有壁厚(a、d1、d2)并在内部空间(IR)中连接到至少两个轮辐(S1、S2、S3、S4)的圆柱形滚筒外壳(M),该至少两个轮辐在径向方向上延伸,并且彼此以距离(b)布置,如在滚筒(5)的轴向方向上所见的。为了最小化在高离心力作用下滚筒外壳直径范围的变化,提出了滚筒外壳(M)在与相应轮辐(S3、S4)的连接区域(V1、V2)中的壁厚的尺寸(d1)应当比在该连接区域(V1、V2)外部的壁厚更大,使得如在滚筒的轴向方向上所见的,滚筒外壳的壁厚(d1)至少在轮辐(S3、S4)之间的区域中从相应轮辐的连接区域开始连续减小到最小壁厚(d2)。(The invention relates to a drum (5) for a carding machine (1), comprising a cylindrical drum shell (M) having a wall thickness (a, d1, d 2) and being connected in an interior space (IR) to at least two spokes (S1, S2, S3, S4) which extend in a radial direction and are arranged at a distance (b) from one another, as seen in the axial direction of the drum (5). In order to minimize the variation of the diameter range of the drum shell under the action of high centrifugal forces, it is proposed that the dimension (d 1) of the wall thickness of the drum shell (M) in the connection region (V1, V2) with the respective spoke (S3, S4) should be larger than the wall thickness outside this connection region (V1, V2), so that the wall thickness (d 1) of the drum shell decreases continuously from the connection region of the respective spoke to the minimum wall thickness (d 2) at least in the region between the spokes (S3, S4), as seen in the axial direction of the drum.)

1. A drum (5) for a carding machine (1), comprising a cylindrical drum shell (M) having a wall thickness (a, d1, d 2) and connected in the inner space (IR) to at least two spokes (S1, S2, S3, S4) extending in a radial direction, and are arranged at a distance (b) from each other, as seen in the axial direction of the drum (5), characterized in that the dimension (d 1) of the wall thickness of the drum shell (M) in the connection region (V1, V2) with the respective spoke (S3, S4) is greater than the wall thickness outside this connection region (V1, V2) so that, as seen in the axial direction of the drum, the wall thickness (d 1) of the drum shell decreases from the connection region of the respective spoke to a minimum wall thickness (d 2) at least in the region between the spokes (S3, S4).

2. Cylinder (5) for a carding machine according to claim 1, characterised in that the wall thickness of the cylinder shell (M) decreases continuously, as seen in the axial direction of the cylinder, starting from the respective spoke (S3, S4), on both sides of the respective connection region (V1, V2) to a minimum wall thickness (d 2).

3. The drum (5) for a carding machine (1) of any of claims 1 or 2, characterised in that the reduction of the wall thickness of the drum shell (M) is continuous.

4. The drum (5) for a carding machine (1) of any of claims 1 or 2, characterised in that the reduction of the wall thickness of the drum shell (M) is in the form of a curve.

5. Cylinder (5) for a carding machine (1) according to claim 4, characterised in that the reduction in the wall thickness of the cylinder shell (M) is in the form of a parabola (P).

6. Drum (5) for a carding machine (1) according to any of the preceding claims, characterized in that the greater dimension (d 1) of the wall thickness of the drum shell (M) in the connection region (V1, V2) with the respective spoke (S3, S4) is between 5.0mm and 25.0 mm.

7. Cylinder (5) for a carding machine (1) according to any of the preceding claims, characterised in that the minimum wall thickness (d 2) of the cylinder shell (M) is between 2.0mm and 15.0 mm.

8. Drum (5) for a carding machine (1) according to any of the preceding claims, characterized in that at least one partial section (T) of the drum shell (M) has a minimum wall thickness (d 2) between the spokes (S1, S2), as seen in the axial direction of the drum (5), so that the length (S) of the partial section (T) amounts to between 5% and 80% of the distance (b) between the connecting areas (V1, V2) of two connecting spokes (S3, S4).

9. Cylinder (5) for a carding machine (1) according to any of the preceding claims, characterized in that the distance (b) between the connection regions (V1, V2) of two adjacent spokes (S3, S4) is between 400mm and 1300mm, as seen in the axial direction of the cylinder.

10. Carding machine (1) with a drum (5) according to any of the previous claims.

Technical Field

The invention relates to a drum for a carding machine, comprising a cylindrical drum shaft having a wall thickness and connected to at least two spokes which extend in a radial direction in an inner space and are arranged at a distance from one another, as seen in the axial direction of the drum.

Background

In order to obtain the most efficient possible carding effect, the carding gap, in particular the main carding zone between the carding clothing at the top of the card and the carding clothing of the carding cylinder (also called cylinder or cylinder), must be minimized. The card clothing of the card cylinder is applied to the outer circumference of the card cylinder by means of special winding and fastening methods. In order to achieve high production, the rotational speed of the carding drums has become higher in recent years. In other words, carding drums with a rotational speed of more than 600rpm have been used simultaneously.

The increase in the rotational speed leads to higher centrifugal forces acting on the cylinders of the carding machine (carding cylinders), which in turn leads to irregular elastic deformations in the diameter range of the carding machine cylinders due to the irregular stresses generated.

As described herein, since irregular elastic deformation occurs in the cylinder region, the comb gap that has been set when the machine is not in operation may be changed while in operation, thereby causing degradation of the comb quality due to a reduction in the comb surface area and causing the comb clothing to collide, thereby damaging the comb clothing.

Various solutions to these problems have been proposed in the patent literature. European patent EP 0446006 a1 proposes a cylinder for a carding machine, wherein the cylinder consists of profiles of light-weight design. In this embodiment, the mass of the drum may be reduced in some cases, thereby reducing the centrifugal force generated thereby. However, this embodiment is very complex and expensive and also requires labor intensive assembly work.

Furthermore, DE 102004035771 a1 proposes an embodiment in which the cylinders of the carding machine are made at least partially of steel or aluminum, which is encapsulated by a carbon fiber-reinforced plastic tape. On the one hand, this will affect the thermal expansion, and on the other hand, this will also reduce the mass with respect to the centrifugal forces generated. This embodiment is also relatively complex and expensive to manufacture.

Disclosure of Invention

The object of the present invention is therefore an apparatus which eliminates the disadvantages of the known prior art, while also allowing a higher rotational speed of the cylinders in the carding without causing undesirable irregular deformations in the area of the circumference of the carding cylinders.

This object is achieved by a drum having the features of the independent claim, wherein a drum for a carding machine is proposed, which drum has a cylindrical drum shell with a certain wall thickness, which drum is connected in an interior space to at least two spokes, which spokes extend in a radial direction and are arranged at a pair of distances from one another, as seen in an axial direction of the drum, wherein the wall thickness of the drum shell in a connection region with the respective spoke is greater than the wall thickness outside this connection region, and wherein the wall thickness of the drum shell starting from the connection region of the respective spoke, as seen in the axial direction of the drum, continuously decreases to a minimum wall thickness at least in the region between the spokes. This compensates for the centrifugal expansion over the entire longitudinal section. The reduction of the wall thickness is carried out at an angle of 0.5 to 2.0 degrees, preferably 1.2 degrees.

Thus, by a simple and inexpensive embodiment, the strength of the drum wall is also increased in the area between the spokes, so that any deformation of the drum wall in this area due to centrifugal forces is distributed to allow a uniform centrifugal expansion.

It is further proposed that the wall thickness of the drum shell should be continuously reduced from the respective spoke to a minimum wall thickness on both sides of the respective connecting region, as seen in the axial direction of the drum.

Thus, areas of the drum wall extend outwardly from the respective connection areas of the spokes in the direction of the respective front face of the drum.

The reduction in the wall thickness of the drum shell in the region between the spokes is preferably implemented as a curved shape, so that an optimum distribution of the generated centrifugal forces is possible. It is advantageously provided here that the curved shape is designed in dependence on the local stresses such that the shape of the curve comprises a constant value of the stresses caused by the centrifugal forces. In simplified form, it may be parabolic.

It is further proposed that the major dimension of the wall thickness of the drum shell in the region of the connection with the respective spoke should be in the range between 5.0mm and 25.0 mm. It is advantageously provided that the minimum wall thickness (d 2) of the drum shell (M) should be between 2.0mm and 15.0 mm. The wall thickness of the drum should therefore have such dimensions that high rotational speeds are also permitted without irregularities in the carding gap being caused with regard to increased centrifugal forces. When the cylinder diameter is greater than 1.0m and the axial length is greater than 1.0m, the minimum wall thickness is preferably 12.5mm and the wall thickness in the connecting region is 22.5 mm.

As a further embodiment of the invention, it is proposed that at least one partial section of the drum shell should have a minimum wall thickness between the spokes, as seen in the axial direction of the drum, such that the length of the partial section is between 5% and 80% of the distance between the connection regions of two adjacent spokes. In order to achieve a compact and stable design of the drum, it is further proposed that the distance between the connection areas of two adjacent spokes should be between 400mm and 1300mm, as seen in the axial direction of the drum.

The use of a cylinder according to the invention in a carding machine is proposed.

Drawings

Further advantages of the invention are shown in the figures and are described in more detail below according to exemplary embodiments:

figure 1 shows a schematic side view of a carding machine;

figure 2 shows a schematic cross-sectional view a-a of the known carding machine according to figure 1;

fig. 3 shows a schematic cross-sectional view of the carding drum according to fig. 2 with an embodiment designed according to the invention;

fig. 4 shows in a partially enlarged view a further embodiment of a carding drum according to the invention as shown in fig. 3.

Detailed Description

Fig. 1 shows a carding machine 1 with a feed chute 2, through which feed chute 2 fibrous material in the form of non-woven fibres is supplied from a feed roll 3. From the feed roll 3 the fibrous material is sent to a lickerin roll 4, which transfers the fibrous material to a carding cylinder 5 (simply "cylinder") of the carding machine 1. Due to the rotary motion (indicated by the arrow) of the drum 5 about its axis (W axis), the fibrous material entrained by the drum 5 is moved and enters the region of the main carding zone 7, which main carding zone 7 is formed in combination with the rotating flat unit 6 rotating above the drum 5. The direction of rotation of the rotating flat unit 6 is indicated by an arrow. The rotating flat unit 6 is provided with a schematically shown rotating flat bar D which is loaded with a card clothing (not shown).

After the main carding zone 7, the carded fibre material enters the area of a rotatably mounted doffer 8, which transfers the fibre material removed from the drum 5 to a rotatably mounted stripping roller 9. The stripping roller 9 carries the fibrous material removed from the doffer 8 by means of a guide device (not shown in detail) to a downstream pair of press rollers 10, which pair conveys the fibrous material to a non-woven hopper 11 by means of additional guide means (for example, a transverse conveyor belt, not shown). The fibrous material (in the form of a fiber sliver) formed in the nonwoven hopper 11 is calendered by the downstream pair of calendering rolls 12 and sent to a sliver winding unit (not shown).

Fig. 2 shows a cross-sectional view a-a of the drum 5 according to fig. 1. The drum 5 is provided with a card clothing G on its outer circumferential surface U1, which card clothing is schematically shown in fig. 2. The drum 5 is mounted on a shaft W and is rotatable in the frame of the card by bearings L1, L2. The shaft W is connected to the drive of the card (not shown). The drum 5 shown here is known and has a cylindrical drum shell M with a constant wall thickness a. The drum shell M is supported in its interior space IR on the shaft W by means of spokes S1, S2 (also referred to as drum bottom), which spokes S1, S2 are located at an axial distance b from one another and have a rotationally fixed connection to the shaft. The spokes S1, S2 are fixed to the inner circumferential surface U2 of the drum shell M in the circumferential connection region V1 and/or V2. The fastening may be accomplished by welding (schematically indicated), by press fitting, or by some other method. It is also possible for the spokes S1, S2 to be designed integrally with the drum shell (e.g., by casting methods).

Fig. 3 shows a longitudinal section through the drum 5, which shows an embodiment of a drum shell M designed according to the invention and having spokes S3, S4 in its interior space IR. The drum shell M has a wall thickness d1 in the connection regions V1, V2 with the respective spokes S3, S4. As seen in the axial direction of the drum 5, starting from the respective connection region V1, V2, the wall thickness of the drum shell M decreases continuously to a minimum wall thickness d2 on both sides of the connection region V1, V2. The inner circumferential surface U2 starting from the inner surface IF of the respective connection region V1, V2 extends at an angle c1 and/or c 2. The angles c1 and c2 may be different or the same. In the present exemplary embodiment of fig. 3, a partial section T of the drum shell M having a length s is provided with a constant wall thickness d 2.

As already described in the embodiment in fig. 2, the spokes S3, S4 in the embodiment in fig. 3 are also located at an axial distance b from one another and are supported on the shaft W, to which they are rotationally fixedly connected. The shaft W is rotatably mounted in the frame by bearings L1, L2 and is connected to a drive (not shown).

As shown in the example in fig. 3, since the wall thickness of the drum shell M is continuously reduced, starting from the respective connection regions V1, V2 of the spokes S3, S4, the centrifugal forces acting on the drum shell M during operation are better absorbed and therefore dissipated, so that the deformations are smaller in the diameter region, in particular in the region between the spokes S3, S4.

The enlargement in fig. 4 shows a partial section of the drum according to fig. 3, wherein in a further embodiment the wall thickness d1 in the respective connecting region V1 is reduced to the minimum wall thickness d2 in the shape of a curve P. This embodiment enables the generated centrifugal forces occurring in the drum shell M during operation to be optimally taken up and/or dissipated.

However, within the scope of the invention, another embodiment is also possible, such as for example making the wall thickness of the drum shell M taper in a parabolic manner (fig. 4) starting from the respective connecting region V1, V2 in the region of the drum shell M between the spokes S3, S4, while the wall thickness of the drum shell decreases continuously from the respective spokes S3, S4 to the respective front face of the drum, as shown in the example of fig. 3.

Other embodiments are also possible, such as embodiments in which there is no central section T with a uniform wall cross-section. In other words, in this case, the tapering of the wall thickness of the drum shell M will lead from the connecting regions V1, V2 to the center of the drum.

List of reference marks

1 carding machine

2 feeding chute

3 feed roll

4 licker-in unit

5 carding cylinder (Cylinder)

6 rotating flat unit

7 main cotton carding area

8 doffing device

9 peeling roller

10 press roll pair

11 nonwoven hopper

12 calendering roller pair

D flat bar

G cotton carding card clothing

IF inner surface

IR inner space

M roller shell

P parabola

S1-S4 spoke

T partial section

U1 outer circumferential surface

U2 inner circumferential surface

V1, V2 junction region

W-axis

a thickness of the outer shell

b spoke spacing

c1, c2 angle

d1 wall thickness

d2 minimum wall thickness

s partial segment length