JPH0248654B2 - CHOKOSOKURINGUSEIBOKINOKAITENRINGUSEIDOSOCHI - Google Patents

Description

[Detailed description of the invention]

INDUSTRIAL APPLICATION FIELD The present invention relates to a rotary ring braking device for an ultra-high-speed ring spinning machine, and more specifically, the rotation of the rotary ring is started and stopped by a command from a spindle rotational speed change program of the ultra-high-speed ring spinning frame. This invention relates to a rotating ring braking device for smoothly starting and stopping spinning. Conventional technology When increasing the speed of a ring-type spinning machine, in order to reduce the frictional resistance between the ring and the traveler,
A method has been proposed in which the ring is rotatably supported via an air bearing. It has a significantly higher spindle speed compared to conventional spinning machines with fixed rings [e.g.
30,000rpm to 50,000rpm], it can exhibit remarkable effects in improving productivity and reducing manufacturing costs. Problems to be Solved by the Invention By using a rotating ring floatingly supported by an air bearing as described above and reducing the relative speed between the traveler and the rotating ring during steady spinning, frictional resistance is increased. It is possible to effectively avoid troubles such as scattering or burnout of the traveler caused by this, or frequent occurrence of thread breakage caused by these obstacles. However, it is an undeniable fact that spinning machines equipped with rotary rings are accompanied by unique problems as described below. That is, since the coefficient of friction between the air bearing and the rotating ring supported in a floating state by the air bearing is extremely small, the rotating ring starts rotating even with a very small spinning force when starting the spinning machine.
A normal balloon cannot be formed and thread breakage occurs. Additionally, if no braking force is applied to the rotating ring when the spinning machine is stopped, the spindle may become unstable due to frictional resistance between the spindle, which is rotatably supported by the spindle insert, and the bearing member of the spindle insert. On the other hand, the rotating ring is essentially in a non-braking state even after the spindle has stopped, and as a result of continuing to rotate due to inertia, the spun yarn winds around the spindle that has already reached the stopped state. The thread will break. In order to avoid such a problem, it is necessary that the rotation ring starts rotating after the spindle rotation speed increases to the set rotation speed, and that the inert rotation of the rotation ring is substantially stopped when the rotation speed of the spindle decreases to the set rotation speed. There is.
In this way, a braking force smaller than the permissible radial load of the air bearing is transmitted from the plurality of brake shoes to the rotary ring, and the rotary ring starts rotating later than the rotation of the spindle, and starts rotating before the spindle stops rotating. There has been a demand for the installation of a rotary ring braking device that stops all spindles at once to completely stop the machine, and in response to this demand, various types of braking devices have been proposed. However, conventional braking devices generally have a complicated structure, which has been recognized as a major limitation in improving the productivity of ultra-high-speed ring spinning machines and improving the quality of spun yarn. In view of the above circumstances, the present applicant developed a parallel link system and a rubber tube that inflates the tube at a position corresponding to each brake shoe by supplying compressed air to the rubber tube as a method for simultaneously operating multiple brake shoes. Braking force is obtained by
The patent application No. 61-45885 [filed on March 3, 1986] was filed earlier. Theoretically, the parallel link system and tube system can move the brake shoes toward and away from the rotating ring of each weight at the same time, but in reality, in the parallel link system, the gap around the link pin is Variations in braking force and braking time occur due to variations in the dimensions of each link, etc., and to completely eliminate this, strict quality control of the equipment is required, which raises issues such as increased costs. Furthermore, with the tube method, there are variations in the wall thickness and internal composition of each part of the tube, and there are also variations in the time when the compressed air pressure occurs due to differences in distance from the supply source. It was recognized that some issues remained. The main object of the present invention is to eliminate variations in braking force and braking time with a relatively simple configuration;
An object of the present invention is to provide a rotary ring braking device for an ultra-high-speed ring spinning machine that allows easy adjustment of braking force and easy setting of optimum braking force. Means for Solving the Problems In view of the above object, the present invention provides an ultra-high speed ring spinning machine having a rotating ring rotatably supported in a floating manner via an air bearing attached to a ring rail. Rotating ring braking for an ultra-high-speed ring spinning machine in which the brake shoe is arranged point-symmetrically with respect to the center of the rotating ring, and the brake shoe is moved toward and away from the center of the rotating ring by a rack-and-pinion mechanism at an equal distance. The gist is the device. By using the rack and pinion mechanism, the brake shoe can be pressed against and separated from the rotating ring of each weight at the same time, eliminating variations in braking force and braking time [start/release]. . By arranging the brake shoes point-symmetrically with respect to the center of the rotating ring, during braking, the brake shoes contact the rotating ring while maintaining point symmetry to apply braking, and the rotating ring There is no unbalanced load applied to the air bearing components, and contact seizure of the air bearing components can be prevented. Further, by rotating the pinion forward and backward with a rotary air cylinder, braking is started and released on the rotary ring, so that a compressed air supply source such as a pneumatic clearer device attached to the spinning machine can be shared. In addition, since the braking force can be adjusted by air pressure,
The optimum braking force can be appropriately selected and its adjustment is easy. Furthermore, the rotary air cylinder is actuated by a solenoid valve, and this solenoid valve is controlled by a voltage detection relay of the spindle drive motor, so that the brake shoe starts braking at the desired spindle rotation speed, and the brake is stopped. It is now possible to release the spinner, which eliminates spinning troubles when starting or stopping spinning. In addition, it is easy to set the optimum braking force,
By applying braking force to the rotating ring in a point-symmetric manner, the rotating ring can be supported by an air bearing with low air pressure. Embodiment FIG. 1 is a plan view of the schematic configuration of the main parts in the first embodiment of the present invention, FIG. 2 is a similar plan view of the second embodiment, FIG. 3 is an explanatory diagram of the drive system, and FIG. The figure is a plan view of the rotating ring assembly, and FIG. 5 is a cross-sectional view taken from the line - - in FIG. 4. In FIG. 1, 1 is a rotating ring, 2 is a pinion, 3 is a rack, 4 is a brake shoe, and 5 is a rod. As shown in FIGS. 4 and 5, the rotating ring 1 is
A predetermined air gap is formed in a bearing housing 1a made of SUS material through a porous air bearing element 1b made of a sintered metal material, and it is integrally connected to a rotating inner ring 1c made of Al material that is rotatably supported. A large number of air bearing elements 1b are attached to a ring rail (not shown) at equal pitches corresponding to each weight through the flange of the bearing housing 1a, and each air bearing element 1b is provided with an air supply port plug 1d. The brake shoe 4 of the present invention is made to correspond directly to the outer periphery of the lower end of the rotating inner ring 1c, or alternatively, another brake drum is connected to the lower end of the rotating inner ring 1c, and the brake shoe 4 is made to correspond to the lower end of the rotating inner ring 1c. It is something that makes you Pinions 2 and racks 3 are installed between each of the rotating rings 1 or every two rings (Fig.
3 will be provided. That is, the pinion 2 rotatably supports the shaft 6 directly on the ring rail or on a bracket (not shown) that can be fixed to the ring rail.
The racks 3, 3 are slidably guided and supported by a bracket (not shown) that can be fixed to the ring rail in a direction perpendicular to the longitudinal direction of the ring rail, and the racks 3, 3 are always symmetrically mounted to the pinion 2. and the rods 5, 5 are fixed to the symmetrical ends of the racks 3, 3. The rods 5, 5 are arranged parallel to the ring rail, and supported movably in a direction perpendicular to the longitudinal direction of the ring rail by the guide support structure of the racks 3, 3; Support is provided by the rod's own guiding support structure used in conjunction with the structure. Brake shoes 4, 4 are symmetrically attached to the rods 5, 5 in correspondence with the rotary ring 1 of each weight. The first embodiment shown in FIG. 1 has the above configuration. Next, in the second embodiment shown in FIG. 2, the racks 3, 3 are directly formed or fixed to the rods 5, 5 of the first embodiment along the longitudinal direction of the rods, and the pinion 2 is directly attached to the racks. 3, 3 may be meshed with each other, but in order to install the racks 3, 3 without any trouble in the space between the rotating rings 1, 1, the racks 3, 3 may be meshed with each other through idle pinions 2a, 2b having the same number of teeth. , both rods 5, 5 are slidably guided and supported parallel to the longitudinal direction of the ring rail, and brake shoes 4, 4 are connected to both rods 5, 5 via arms 7, 7 in the longitudinal direction of the ring rail. It has been set up to correspond to The shafts of the idle pinions 2a, 2b are supported by the same member as the shaft 6 of the pinion 2. Further, the arms 7, 7 accurately transmit the driving force (air pressure) acting on the pinion 2 as braking force to the brake shoes 4, 4. The second embodiment shown in FIG. 2 has the above configuration. Next, the drive system shown in FIG. 3 will be explained. In Fig. 3, 8 is a compressor, 9 is a first
A pressure reducing valve, 10 is a second pressure reducing valve, 11 is a solenoid valve, 12 is a voltage detection relay for the spindle drive motor, 13 is air piping to the air bearing element, 14 is a rotary air cylinder, 15 and 16 are rotary air cylinders Air piping 14 is connected to the ring rail, and 17 is a ring rail to which the rotary ring 1 is attached as described above. Compressed air, which has been reduced to a predetermined pressure by a first pressure reducing valve 9, is distributed and supplied from a compressor 8 to the air bearing element portion of each rotating ring 1 via an air pipe 13, and the air bearing element portion of each rotating ring 1 is constantly rotated during operation of the ring spinning machine. The ring 1 is floatingly supported in a non-contact manner using a predetermined air pressure. The rotary air cylinder 14 is attached with its output shaft (not shown) connected to the shaft 6 of each pinion 2 in FIGS. 1 and 2, and specifically, it is a rotary actuator known as a rotary actuator. It is sufficient to use , and the explanation of its structure will be omitted, but
In FIG. 3, compressed air, which has been reduced to a predetermined pressure from the compressor 8 by the first pressure reducing valve 9 and the second pressure reducing valve 10, is passed through the solenoid valve 11 to both air pipes 15,
By selecting and supplying either one of 16, the brake shoes 4, 4 are moved toward and away from the rotary ring 1 through the pinion 2 and the racks 3, 3 by rotating in the forward and reverse directions to start braking and release the brake. It is something that can be done. The means for selecting both the air pipes 15 and 16 are various types of ON instead of the solenoid valve 11.
-OFF control device may also be used. Table 1 below shows an example of the operating conditions of the rotary actuator when spinning cotton for 40 ^seconds with a twist coefficient of 3.64 and a spindle rotation speed of 31,500 rpm.

[Table] Both types of the two examples have an air pressure of 2.5~
It shows that it can operate at 3.0 kg/cm ² and can brake within 1 second with a braking force of 1/6 to 1/7 of the air bearing's static load capacity of 3 kgf. The solenoid valve 11 is controlled by detecting the voltage consumption, current consumption, power consumption, etc. of the spindle drive motor, or by detecting the rotational speed of the spindle drive shaft. For example, FIG. 6 shows an example of the control. It shows. That is, in Fig. 6, the vertical axis is the spindle rotation speed [rpm], and the horizontal axis is time, where A indicates the start of spinning, B indicates the release of braking of rotating ring 1, and C indicates the start of braking of rotating ring 1. , D indicate each point in time when spinning is stopped. In the same figure, a comparison table is shown at the bottom of the rotary ring 1 between the air bearing supported type and the brain bearing supported type, and the spindle after the brake of the rotary ring 1 is released. There is a difference of about 5 times in the time required for the start-up rotation speed, indicating that the air bearing type is smoother. In Fig. 6 above, when the spindle startup speed is 10,000 rpm, the brake of the rotating ring 1 is released,
During the spindle stopping process, the spindle rotation speed increases.
Braking is applied to the rotary ring 1 when the rpm decreases to 12,000 rpm, but this is not a limitation, and braking is started and released on the rotary ring by a control signal according to the spindle rotational speed change program. That is, the present invention suppresses the rotation of the rotary ring 1 until the spindle increases to a constant rotation speed, and when the spindle decreases to a constant rotation speed, the rotation of the rotary ring 1 is suppressed.
This is to suppress the rotation of the balloon and control the balloon, thereby preventing thread breakage. Effects of the Invention According to the present invention, with a relatively simple configuration, it is possible to start and release the braking of multiple spindle rings at the same time without variations in braking force and braking time, thereby improving reliability. In addition, since braking is applied to the rotating ring at point-symmetrical positions, an uneven load is not applied to the rotating ring, and seizure of the air bearing can be prevented. In addition, since the braking force can be adjusted by air pressure,
The optimum braking force can be easily set and changed. Furthermore, since it is possible to start and release the braking of the rotary ring at a desired spindle rotation speed, it is possible to eliminate spinning problems such as yarn breakage when starting or stopping spinning. Furthermore, by accurately setting the braking force of the rotary ring and by not applying eccentric force during braking, the pressure at which the rotary ring is supported by the air bearing can be kept at a low air pressure.

[Brief explanation of drawings]

FIG. 1 is a plan view showing a schematic configuration of the main parts in the first embodiment of the present invention, FIG. 2 is a similar plan view of the second embodiment, FIG. 3 is an explanatory diagram of the drive system, and FIG. 4 is a plan view of the rotating ring assembly, and FIG.
FIG. 6, which is a sectional view taken from the - line in the figure, is a graph showing an example of the spindle rotational speed and the braking mode of the rotary ring, and a comparison table with the plain bearing support type is shown below. 1... Rotating ring, 2... Pinion, 3... Rack, 4... Brake shoe, 5... Rod, 8
... Compressor, 11 ... Solenoid valve,
12... Spindle drive motor voltage detection relay, 14... Rotary air cylinder, 17... Ring rail.

Claims (1)

[Claims] 1. In an ultra-high-speed ring spinning machine having a rotating ring that is rotatably supported in suspension via an air bearing attached to a ring rail, the brake is arranged point-symmetrically with respect to the center of the rotating ring. 1. A rotary ring braking device for an ultra-high-speed ring spinning machine, characterized in that the brake shoe is equipped with a rack and pinion mechanism that moves the brake shoe toward and away from the center of the rotary ring by an equal distance. 2. The rotary ring braking device for an ultra high-speed ring spinning machine as set forth in claim 1, wherein multiple brake shoes are arranged on a common rod in correspondence with each rotary ring. 3. Claim 1, wherein the means for rotating the pinion is a rotary air cylinder.
A rotary ring braking device for an ultra-high-speed ring spinning machine as described in 2. 4. The rotary ring braking device for an ultra-high speed ring spinning machine according to claim 3, wherein the means for operating the rotary air cylinder is a solenoid valve. 5. The rotary ring braking device for an ultra-high-speed ring spinning machine according to claim 4, wherein the means for operating the solenoid valve is a voltage detection relay of a spindle drive motor. 6. The rotary ring braking device for an ultra-high speed ring spinning machine according to claim 1, wherein the means for adjusting the braking force is pneumatic pressure. 7. The rotary ring braking device for an ultra-high-speed ring spinning machine according to claim 1, wherein braking is started and released on the rotary ring in response to a control signal according to a spindle rotational speed change program.