DE10128077A1 - Spinning machine has rotating cylinder with internal pneumatically-adjusted mass balance actuator mechanism operating at cylinder natural frequency - Google Patents

Abstract

A textile or spinning machine has an elongated cylindrical rotary thread guide (1) with a mass balance (2). The guide esp. has an mechanism (3) to adjust the mass balance position, minimising vibration. The adjustment mechanism alters the mass balance axial position and is moved by an actuator (23) along a linear guide (4). the cylinder has an internal cylinder operated as a mass balance and moved by external pneumatic action. In a preferred embodiment the cylinder has an elastic external mantle which expends under pneumatic action to lock the piston in place. In an alternative embodiment the mass balance weight is altered by injection or withdrawal of a quantity of liquid to or from a reservoir.

Description

The invention relates to a device for guiding, treatment or recording a running thread with an elongated cylindrical rotation body according to the preamble of claim 1 and a method for leg Flow of vibrations in such a device according to the Oberbe handle of claim 12.

In spinning systems or textile machines, such devices are in under of different types and shapes used to guide one or more threads treat or record. Such devices are called godets used for conveying, stretching or heating threads become. Devices are also known which are used when winding a thread as a pressure roller, guide the thread to a bobbin surface. However, there are also known devices, which in a winding machine as a bobbin holder Wind up a large number of threads to form a bobbin. All mentioned devices tungen have in common that an elongated cylindrical body of rotation is used to guide, treat or on the thread or threads increase. The elongated cylindrical rotary body can be a be rotatably supported on one side or on both sides, so that it rotates is cash. To achieve high thread speeds of more than 6,000 m / min For example, depending on the diameter of the coils, a bobbin holder must be Start to end of winding into a spool with a speed range of approx.  Run through 2,000 rpm to 30,000 rpm. In particular, dimensions, the critical speeds that an undamped vibration of the rotary body pers cause, be avoided to the one-sided bearing of the rotation not destroy the body. A critical speed exists when the exciter fre frequency coincides with the natural frequency of the rotating body. The Eigenfre sequences are dependent on the geometrical and material-technical conditions (E- Module) depending on the bearing stiffness and the masses of the system. The resul The amplitudes of the excitation frequency are the natural frequencies of the system stems, the unbalance masses and the damping of the system.

EP 0 234 844 describes one for influencing the vibrations Apparatus known, in which the rotating body has several balancing masses has to the unbalance masses and thus the resulting vibration to reduce plitches. This is a very lengthy and costly end balancing necessary to achieve the required balancing quality. If during the life cycle of a device new imbalances on the rotating body a new balancing may be necessary. As with maintenance-related disassembly and subsequent assembly must be carried out in which renewed unbalance could be generated.

Another device is known from DE 42 40 920 A1, in which the occurring vibrations are dampened by the use of a damper become. A vibrati is in the machine frame of the device for damping arranged on absorber. Such vibration absorbers show only in one relative narrowed frequency range an optimal damping behavior. With that is ever but not possible to vibrate out over an entire speed range enough to dampen. On the contrary, the areas of critical speed len only shifted in frequency. On the other hand, there is a high level of technical Effort required to achieve the required damping values in particular Operation of the device in the range of natural frequencies. moreover  mechanical energy is converted into thermal energy through friction delt, which can lead to further disadvantages.

The invention has for its object a device with a langge stretched cylindrical rotating bodies as well as a method of influencing solution to create vibrations in such a device in which or by which an operation of the rotating body in the area of its eigenfre sequences is avoided without changing the operating speed range.

The object of the invention is achieved by a device with the features according to claim 1 and by a method having the features of claim 12 solved.

The invention goes entirely over the known devices new solution. The resulting vibrations are not ge dampens or reduces the unbalance, but it prevents the Rotati body is operated in the range of the natural frequencies. For this purpose, the Be the nature of a balancing mass attached to the rotating body changed that an increase or decrease in the natural frequency of the Rotati body occurs. Through such a frequency shift of the natural frequency can the occurrence of critical speeds within the operating speed range advantageously avoided. For this purpose, a compensation device on the ro station body trained to change the balancing mass for the purpose the influence of the natural frequency of the rotating body changed.

There are basically two options for changing the balancing weight. In a first variant, the position of the balancing mass is preferably in Changed longitudinal direction of the rotating body. This allows the compensation Position the mass in any position on the rotating body, so that an optimal Influencing the natural frequency is guaranteed.  

The compensation device is advantageous here by a linear guide, in which the balancing mass is movably guided, and a motion actuator formed to move and fix the balancing mass. This training is especially for long cantilevered rotating bodies such as coils holder or pressure rollers advantageous.

The linear guide could in this case be within the rotating body arranged cylinders can be formed. In the cylinder is designed as a piston Dete balancing mass arranged movably. To move and fix the Piston, the motion actuator is formed by a pneumatic unit which is connected by means of lines to at least one end of the cylinder. This means that any position within the cylinder of the piston or of the balancing mass. The pneumatic unit is located outside the rotating body.

In a particularly advantageous development, the piston has an elastic on the jacket, which a mini paint diameter or a maximum diameter. The ma Dimension the maximum diameter so that the piston inside the cylinder is fixed.

In a second basic variant for influencing the compensation mass is proposed, the weight of the balancing mass on the rotation change body. By increasing or decreasing the weight of the Compensating mass on the rotating body can be the natural frequency of the rotation affect the body in the desired manner.

A particularly simple embodiment is the advantageous further development of the invention according to claim 7. Here, the compensation device by ei NEN storage in which the balancing mass formed as a fluid is acceptable and formed by a drain actuator to promote the fluid. Depending on  desired state of the balancing mass is in through the drain actuator fluid pumped the reservoir or a certain amount of fluid from the reservoir conveyed out.

In order to allow a fixed clamping of the amount of fluid, the invention is appropriate device according to the features of claim 8 educated det. In this case, the storage is made by a pressure chamber within the rotation body formed. The pressure chamber contains a movably guided pressure ring, which seals the pressure chamber from a fluid inlet. The fluid inlet is connected to the drain actuator arranged outside the rotary body. Thus, when the fluid is conveyed, the pressure ring is inside the pressure chamber shifted towards an air or gas cushion.

The drain actuator is advantageously a partially filled with a fluid Containers and a controllable pressure source are formed. By an overpressure in the Containers can be a certain amount of fluid advantageous in the pressure chamber promote. Here, the overpressure within the container can be directly in the Liquid or through an air or gas cushion inside the container become.

In principle, however, there is also the possibility to ver the two variants knot so that the balancing mass can be changed in position and weight.

To ensure that no critical over the entire speed range State is reached, according to an advantageous development of the Erfin the vibration of the rotating body by a vibration sensor measure up. The vibration sensor and the compensation device are Change of the balancing mass coupled via a control unit. So read targeted changes can be made in good time without major delay Initiate the rotating body.  

Further training is to influence the higher order natural frequencies of the invention according to claim 11 particularly advantageous. Here, several Compensating masses are changed simultaneously on the rotating body, so that higher waveforms advantageously shifted to non-critical areas can be.

Some embodiments of the device according to the invention and that he Methods according to the invention are with reference to the accompanying drawings described in more detail.

Show it

Figures 1 and 2 schematically a first embodiment of the device according to the invention;

Fig. 3 schematically shows another embodiment of the device according to the invention;

Fig. 4 shows schematically two modes of natural vibration of a bilaterally gela rotated body;

Fig. 5 shows schematically a natural vibration form of a rotating body mounted on one side.

In Fig. 1 and 2, a first embodiment of the pre direction invention is shown schematically. Fig. 1 shows a sectional view in the longitudinal direction, wherein only the essential components of the device for the invention are shown ge. FIG. 2 shows a detailed view of the exemplary embodiment according to FIG. 1. The following description applies to both FIGS. 1 and 2, insofar as no express reference is made to one of the figures.

The embodiment of the device has a long cantilever-shaped rotary body 1 . The rotary body 1 is rotatably supported at one end by a support 24 through the bearings 25 . Devices of this type are used as godets or overflow rollers for guiding and conveying threads. The rotary body 1 could be driven with an electric drive (not shown here). However, it is also possible for the rotary body 1 to be driven to rotate by friction.

A compensating mass 2 is arranged in the interior of the rotating body 1 and is adjustable in the longitudinal direction of the rotating body 1 by means of a compensating device 3 . For this purpose, the balancing mass 2 leads in a linear guide 4 ge. The linear guide is designed as a cylinder 7 which extends in wesentli Chen over the entire length of the rotary body 1 . Inside the Zy cylinder 7 , the balancing mass designed as a piston 6 is guided. At the end of the cylinder 7 facing the end of the bearing, an opening 12 is provided, which is connected via a channel 11 and a line 10.1 to a pneumatic unit 5 . At the opposite end of the cylinder 7 , an opening 15 is formed, which is formed via the annular chamber 14 , via a groove system 13 , the rule between the cylinder 7 and the jacket 8 of the rotating body 1 and a channel 42 , with the line 10.2 and Pneumatic unit 5 connected. For this purpose, a rotary union 43 is formed in the carrier 24 between the line 10.2 and the channel 42 at the bearing end of the rotary body 1 . The pneumatic unit 5 , which represents the movement actuator for changing the position of the balancing mass 2 , is coupled via the control unit 23 to a vibration sensor 22 provided at the bearing end of the rotary body 1 .

The piston 6 guided in the cylinder 7 , which forms the balancing mass 2 , is shown in more detail in FIG. 2. Here, FIG 2.1 2.2 Fig. 6 the piston in a non-fixing th state and Figs. In a fixed state within the cylinder 7.

The piston 6 has a sliding plate 16.1 and 16.2 on the end faces, which are sealingly guided in the cylinder 7 . A compression spring 17 is clamped between the sliding plates 16 . The sliding plates 16.1 and 16.2 are held together by an elastic jacket. The interior defined by the jacket 18 and the sliding plates 16.1 and 16.2 is filled with a fluid 19 .

During the operation of the rotary body 1 , the piston 6 is first fixed in a preselected position within the cylinder 7 , as shown in Fig. 2.2 Darge. For this purpose, an excess pressure p ₁ is generated via the pneumatic unit 5 in the cylinder 7 on the end of the piston facing the end of the bearing and an internal pressure p ₂ on the opposite side of the piston 6 . The pressures p ₁ and p _{2 are set} such that the force resulting from the pressure difference is greater than the force exerted by the compression spring. Thus, the sliding plates 16.1 and 16.2 are pressed against each other, so that the clamped fluid 19 transfers the jacket 18 from a minimum diameter to a maximum diameter. The elastic jacket is pressed against the inner wall of the cylinder 7 . The piston 6 is firmly connected to the cylinder 7 . No relative movement is possible, so that the mass of the piston 6 is technically fully effective in terms of vibration.

During the operation of the rotary body 1 , the signals of the vibration sensor 22 are received and evaluated by the control unit 23 . In the event that an excitation frequency is found that comes close to a Eigenfre frequency, the pneumatic unit 5 is activated via the control unit 23 . The pressure difference between the overpressures p ₁ and p ₂ is changed so that the sliding plates 16.1 and 16.2 are first pushed back into their starting position by the compression spring 7 . Now can be increased by increasing the overpressure p _{1 of} the piston 6 within the cylinder 7 towards the free end of the rotating body 1 , as shown in Fig. 2.1. For example, the piston 6 could be located on the stop 20 . The overpressure is p ₁ <p ₂ . The force resulting from the pressure difference, which acts on the piston 6 , is greater than the spring force, so that the piston 6 is fixed to the stop 20 within the cylinder 7 . This results in a specific natural frequency of the rotation body. When the excitation frequency approaches the natural frequency of the rotating body 1 , which is signaled by the vibration sensor 22 of the control unit 23 , the pressure setting in the cylinder 7 is changed such that the pressure p ₁ <p _{2 is} set. The force resulting from the pressure difference is smaller than the spring force, so that the piston, as shown in Fig. 2.1, is in the relaxed state. The piston 6 is moved to the stroke 21 on the opposite side of the cylinder 7 . As soon as the piston 6 has reached the stop 21 , which is transmitted, for example, via a contact sensor of the control unit, the pressure difference is changed such that the piston is fixed in the cylinder 7 . The rotary body 1 thus has a changed natural frequency.

In Fig. 3, another embodiment of a Vorrich device according to the invention is shown schematically, the parts essential to the invention are shown in a sectional view. In Fig. 3.1 the device is shown in a state in which the rotary body has a minimal balancing mass. In Fig. 3.2, however, the state with maximum equalization is shown. The following description applies to both Figs. 3.1 and 3.2.

The embodiment of the device has a long overhanging Rotati on body 1 , which is mounted in the carrier 24 . The rotational body 1 is not shown in its entire length, which is symbolized by a broken line. In this embodiment, a plurality of sle 44 are spanned on the circumference of the rotary body 1 , which each serve to hold a thread. This example of direction is used in winding machines for winding threads.

The rotary body 1 is supported by the bearings 25 in the carrier 24 . A fluid 32 is introduced within the rotating body 1 and acts as a balancing mass on the rotating body 1 . The compensation device 3 consists of a received within the rotary body 1 memory 30 and egg nem container 28 , which is connected via a discharge actuator 29 with a control unit 23 connected. The control unit 23 is coupled to a vibration sensor 22 , which detects the vibrations at the bearing end of the rotary body 1 . A pressure chamber 31 is formed in the accumulator 30 within the rotating body 1 and is sealed by a pressure ring 26 against a fluid inlet 33 opening into the accumulator 30 . The pressure chamber 31 is preferably filled with a gaseous medium.

The fluid inlet 33 is connected via channels 36 and 37 to a fluid outlet 34 on the rotary body 1 . At the bearing end of the rotating body 1 , the fluid outlet 34 opens into a circumferential annular groove 39 which is opposite an annular groove 40 in the carrier 24 . The annular groove 39 and the annular groove 40 are sealed on the rings 27.1 and 27.2 to the outside. The annular groove 40 is connected to the container 28 via a bore 41 with a liquid line 35 . The container 28 is partly filled with the fluid 32 and partly with a gaseous medium. A separation membrane 38 is provided between the gaseous medium and the fluid 32 . The gaseous medium is brought into the container 28 via the outlet actuator 29 , which is designed as a pressure source.

In operation, the rotating body 1 is driven by an electric drive provided at the end of the bearing. In this case, threads tapering onto the stretched sleeves 42 are wound into bobbins. Here, the rotating body 1 could be operated in a state in which the balancing mass has a mini males weight, as shown in Fig. 3.1. In a second state, the rotating body 1 could be placed in a state in which the balancing mass assumes a maximum weight, as shown in FIG. 3.2. Here too, the pressure source 29 can be controlled via the control unit 23 in such a way that the pressure p ₃ present within the container 28 increases or decreases compared to the pressure p ₄ prevailing in the pressure chamber 31 . In the event that p _{3 is} greater than the excess pressure p ₄ in the pressure chamber, the pressure ring 26 in the memory 30 is moved to the opposite stop. The volume of the. Pressure chamber 31 is reduced. In contrast, the absorbed volume of the fluid 32 within the reservoir 30 increases . The weight of the balancing mass was increased so that the natural frequency of the rotating body takes on a different value. The natural frequency of the rotary body 1 can be controlled by controlling the pressure p ₃ . By evaluating the measured by the vibration sensor 22 of the vibration Ro tationskörpers 1, the natural frequency can the rotary body 1 to be changed, so that the operation of the rotating body 1 is prevented in the critical natural frequency range.

To explain the mode of operation, some vibration forms of a two-sided rotating body ( FIG. 4) and a single-sided rotating body ( FIG. 5) are shown in FIGS . 4 and 5. The natural frequencies of a vibrating system always have defined modes. If a mass ml is attached in the areas of the maximum deflections of the respective natural frequency, it has a large influence on the resulting natural frequencies of the rotating body as an inert mass. If the inertial mass m _{1 is} attached to the nodes, it has very little influence. With the system remaining the same, the respective natural frequency drops the closer the mass m _{1 is} in the range of the maximum deflection of the natural frequency.

The positioning of the masses for influencing the first natural frequency of a godet clamped on both sides is shown in FIG. 4.1 and the positioning for influencing the second natural frequency in FIG. 4.2. In order to influence the second natural frequency, the masses m ₁ and m _{2 of} equal size were positioned. With a balancing mass m ₁ , the positioning according to FIG. 4.1 was found with a godet clamped on both sides that the natural frequency could be changed relatively by 17%. In contrast, only a slight change was registered in the second-order natural frequency. By contrast, when using two compensating masses according to FIG. 4.2, a change in the natural frequency of approximately 15% could also be achieved with the second-order natural frequency.

In FIG. 5, the natural oscillation mode of the first order is shown a cantilevered rotary body. The balancing mass m _{1 is positioned} at the clamping end in the upper version and at the free end of the rotating body in the lower version. With such a galette it was found that the change in position of the balancing mass made it possible to change the natural frequency relatively of more than 20%. The effect of the natural frequency shift depends on the one hand on the ratio of the mass of the rotating body to the balancing mass and on the other hand on the positioning of the balancing mass relative to the nodes of the natural frequencies.

The device according to the invention and the method according to the invention are characterized in that the vibration behavior of the rotating body can be influenced without a complex damping system. In the case, that the excitation frequencies change due to changes in operating states (Pro speeds, mass increase during a winding trip) the resonance frequency quenz approaching, this can advantageously be moved so that the Eigenfre frequency still above the excitation frequency or the natural frequency below the excitation frequency.  

LIST OF REFERENCE NUMBERS

1

body of revolution

2

Leveling compound

3

balancer

4

linear guide

5

Movement actuator, pneumatic unit

6

piston

7

cylinder

8th

coat

10

cables

11

channel

12

opening

13

Längsnutensystem

14

annular chamber

15

opening

16

sliding plate

17

spiral spring

18

coat

19

fluid

20

attack

21

attack

22

vibration sensor

23

control unit

24

carrier

25

camp

26

pressure ring

27

seal

28

container

29

Drain actuator, pressure source

30

Storage

31

pressure chamber

32

fluid

33

fluid inlet

34

fluid outlet

35

liquid line

36

channel

37

channel

38

separating membrane

39

ring groove

40

ring groove

41

drilling

42

channel

43

Rotary union

44

sleeves

Claims (15)

1. Device for guiding, treating or picking up a running thread with an elongated cylindrical rotating body ( 1 ) which is rotatably supported at least on one side and which has a balancing mass ( 2 ) for influencing vibrations, characterized in that a balancing device ( 3 ) to change the balancing mass ( 2 ) during operation on the rotating body ( 1 ) is formed, the purpose of influencing the natural frequency of the rotating body ( 1 ) by changing the balancing mass ( 2 ). 2. Device according to claim 1, characterized in that the compensating device ( 3 ) cooperates with the compensating mass ( 2 ) such that the position of the compensating mass ( 2 ) on the rotating body ( 1 ) is preferably changeable in the axial direction. 3. Apparatus according to claim 2, characterized in that the compensating device has a linear guide ( 4 ) in which the compensating mass ( 2 ) is movably guided, and a movement actuator ( 23 ) for moving and fixing the compensating mass ( 2 ). 4. Apparatus according to claim 3, characterized in that the linear guide ( 4 ) is formed by an inside the rotary body ( 1 ) arranged cylinder ( 7 ) which receives the piston ( 6 ) designed as a balancing mass ( 2 ), and that Movement actuator is formed by a pneumatic unit ( 23 ) which is connected to at least one end of the cylinder ( 7 ) by means of lines ( 10.1 , 10.2 ). 5. The device according to claim 4, characterized in that the piston ( 6 ) has an elastic jacket ( 18 ) which by changing loads of the piston ( 6 ) has a minimum diameter or a maximum diameter, the maximum diameter being dimensioned in this way that the piston ( 6 ) is fixed within the cylinder ( 7 ). 6. Apparatus according to claim 1 or 2, characterized in that the compensating device ( 3 ) cooperates with the balancing mass ( 2 ) such that the weight of the balancing mass ( 2 ) on the rotating body is changeable. 7. The device according to claim 6, characterized in that the compensating device ( 3 ) has a memory ( 30 ) in which the as a fluid ( 32 ) designed as a balancing mass ( 2 ) can be received, and a laßaktor from ( 29 ) for conveying the fluid ( 32 ). 8. The device according to claim 7, characterized in that the memory ( 30 ) by a pressure chamber ( 31 ) within the Rotationskör pers ( 1 ) is formed, that the pressure chamber ( 31 ) opposite a fluid inlet ( 33 ) has a movably guided pressure ring ( 26 ) contains, which seals the pressure chamber ( 31 ) against the fluid ( 32 ), and that the fluid inlet ( 33 ) with the outside of the rotating body ( 1 ) arranged drain actuator ( 23 ) is connected. 9. The device according to claim 8, characterized in that the drain actuator is formed by a partially filled with the fluid ( 32 ) container ( 28 ) and a controllable pressure source ( 29 ), the container ( 28 ) with the fluid inlet ( 33 ) of the Memory ( 30 ) is connected. 10. Device according to one of the preceding claims, characterized in that a vibration sensor ( 22 ) for measuring the vibrations of the Rotationskör pers ( 1 ) is provided and that the vibration sensor ( 22 ) and the compensation device ( 3 ) by a control unit ( 23 ) are coupled. 11. Device according to one of claims 1 to 10, characterized in that a plurality of balancing masses are arranged on the rotary body ( 1 ), which cooperate with the balancing device ( 3 ). 12. Method for influencing vibrations in a device for Management, treatment or taking up a running thread, in which a Elongated cylindrical rotating body rotating in operation is driven and in which the rotary body is off before operation was added equally, characterized in that the nature of the off during the operation of the rotating body equally to increase or decrease the natural frequency of the Rotati body is changed. 13. The method according to claim 12, characterized in that the position of the balancing mass preferably in the longitudinal direction of the rotation  body is changed. 14. The method according to claim 12, characterized in that the weight of the balancing mass on the rotating body is changed. 15. The method according to any one of claims 12 to 14, characterized in that the change in the nature of the balancing mass depending on a measured vibration of the rotating body.