LT6746B - Carding mechanism and method of carding machine - Google Patents

Abstract

The present invention discloses a carding mechanism and method of a carding machine, including: a forward feeding mechanism, a licker-in mechanism, a cylinder mechanism, a double-zone flat mechanism, a doffer mechanism, and a three-roller cotton stripping mechanism, where the forward feeding mechanism realizes the feeding of a cotton material, and a card clothing on the surface of the licker-in mechanism grabs a cotton fiber from the fed cotton material during a rotation process; the cylinder mechanism enables the cotton fiber to enter the double-zone flat mechanism after the cotton fiber iscarded through a stationary flat for a first time; the double-zone flat mechanism includes a front-zone flat and a rear-zone flat; the front-zone flat has a line speed opposite to the direction of a line speed of a cylinder, and the rear-zone flat has a line speed in the same direction as the cylinder speed; after the cotton fiber passes through the double-zone flat mechanism and is carded by a stationary flat for a second time, the cotton fiber is transferred to a doffer surface of a doffer mechanism; the three-roller cotton stripping mechanism strips a web off the doffer surface. The present invention greatly reduces the load on a component of each zone and the loss on the power, and significantly improves the capacity of discharging an impurity, thereby greatly improving the production efficiency.

Description

TECHNICAL FIELD

The present invention relates to the field of machine construction, in particular to the heating mechanism and the operation of the carding machine.

BACKGROUND OF THE INVENTION

In the textile industry, a carding machine is used to heat cotton fibers. In the process of turning wool into yarn, the quality of the carding machine determines the quality of the fiber, which means that the carding machine influences the quality of the final product. The working principle of the carding machine consists of feeding the cotton supply equipment to the respective machine, such as a cotton carding machine or a special fiber carding machine, and then the carding machine staples and heats the fibers of the fed material. During the carding process, the wrapped or twisted cotton hairs are gradually straightened and eventually, when exposed to the carding component, turn into individual fibers. The carding machine also has a decontamination function, this task is performed by a receiver, a knife, a small bottom cover and movable lids. An important part of the carding machine is the carding cleaner, which can remove contaminants, short hairs, etc. formed during the previous process. Then, after the carding process, the carding passes through the pressure roller device, becoming a layer which is held in the layer cylinder, and is introduced into the drawing process as a folder.

In recent years, with the continuous improvement of carding technology and the emergence of new carding technologies, the carding system of the carding machine has changed significantly. Currently, two design solutions are widely used: a single movable lid strip system and a fully stationary lid strip system. Both carding system solutions have their own characteristics. With the rapid development of the textile industry, it is especially important to create a carding system that meets high production requirements and at the same time ensure product quality, and this is a broad object of consideration of the design of an improved carding system.

The investigation resulted in the following results of a review of the heating systems available on domestic and foreign markets:

In a locally produced first - generation high - yield A186 type carding machine, the design can only be adapted with one movable lid, ie. with one movable lid strap system. This construction is simple to operate and easy to repair. However, this design is large in size, and because it is a precisely integrated design that moves in a repetitive manner in the chain drive, a large contact surface is formed and the coupling part does not work well with the drum, resulting in very low operating accuracy, high friction speed is limited, which directly changes the quality of the product. This design has significant drawbacks in terms of both production efficiency and energy consumption.

The DK4 type carding machine manufactured by a Swiss company uses a carding system with fully stationary lids. This carding machine does not have a rotary cap design, all caps are stationary. Not all processes are flexible carding, so the carding strength is significantly higher than that of a conventional carding machine using a single belt of rotating lids. In this design, the degree of insertion of the drum caps is significantly better, ensuring the stability of the distance between the two elements, and indirectly ensuring the stability of the technological process and the final product. The distance of the stationary caps can also be adjusted to take into account the different effects of the actual raw materials. This design does not include a cap drive component, which significantly reduces the inertia of the entire machine and the complexity of the drive system, and because there is no wear on the drive component, it significantly reduces the cost of the machine. However, it also has many shortcomings. In particular, because the stationary lid band heaters do not move, the storage time and space of the cotton are inferior to that of a flexible space of conventional construction. Therefore, cotton can easily clog the lid. Cotton tends to accumulate in this small space, which also tends to accumulate contaminants, and the design capacity of the fixed lid design is relatively limited, so to ensure proper long-term operation of the machine, it is necessary to reduce the contaminants in the cotton to a relatively minimum level. , which increases the price of the raw material.

Patent document CN103451779A, published on 03/09/2013, describes a carding mechanism for moving the movable lids of a carding machine.

SUMMARY OF THE INVENTION

To overcome the drawbacks of the prior art, the present invention provides a carding machine carding mechanism that increases the effective carding area and significantly reduces the amount of contaminants or short hairs in the final product, thereby improving production efficiency.

The following technical solutions are used in the present invention to achieve the above object:

The carding mechanism of the carding machine has: a front-direction feeder, a receiver, a drum, a two-zone lid mechanism, a remover and a three-roll cotton removal mechanism, a front-direction feeder feeds cotton and grips cotton

after the cotton fiber is first carded through the strip of stationary lids, the drum introduces the cotton fiber into the two-zone lid mechanism;

the dual zone lid mechanism consists of front zone caps and rear zone caps; the speed line of the front zone caps is opposite to the direction of the drum speed line, and the directions of the rear zone and drum speed lines coincide;

when the cotton fiber passes through the two-zone lid mechanism and the strip of stationary caps is carded a second time, the cotton fiber is transferred to the surface of the remover;

the three-roll cotton removal mechanism removes the card from the surface of the remover.

The front-facing feeder has a cotton feed roller, a pressure cylinder, and a plain bearing seat; a sliding bearing housing is mounted at each end of the cotton feed roller, and each sliding bearing housing has a pressure cylinder;

a latch is mounted on one side of the cotton feed roll and the distance between the cotton feed roll and the latch is adjustable according to the characteristics of the material; a pin is welded to both ends of the cylindrical body of the cotton roll and the stiffening edge is not mounted in the cylindrical body of the cotton roll; there is a groove in the cylindrical body of the cotton supply roll; there is a groove at both ends of the pin.

The pressure cylinder is fitted with a spring; the piston in the lower part of the pressure cylinder is in contact with the corresponding plain bearing seat; the rear cover of the upper part of the pressure cylinder is rotated to compress the spring and thus adjust the pressure of the plain bearing seat.

j a roller bearing is inserted in the middle of the plain bearing seat; the roller bearing is mounted on the left short shaft and the right short shaft; the two short shafts are threaded to each other and there is a short shaft reinforcing bar on the right side of the short shafts; the lowest position of the plain bearing is limited by the bolt and nut under the plain bearing seat.

The receiver has a receiver frame, a receiver connector and a bearing socket;

the receiver connector is welded to the two pins and the receiver cylindrical body, and the stiffening edge is not mounted in the receiver cylindrical body; there is a bearing socket at each end of the receiver connector and a receiver frame mounted on the bearing socket;

a groove is formed at a distance from the left and right edges of the receiver connecting member for pressing and securing one end of the heater set; there is a groove in the sealing ring at the left and right ends of the pins.

the lid zone of the two-zone lid mechanism is divided into two parts, and a string of lids is provided in each zone; each zone has a two-stage cleaning roller in the strip of movable lids; each zone is held by three elements, i. front bracket, support bracket and rear bracket.

The lids are fitted with a set of heaters which is fixed in a clamping slot on both sides; the inner side of the caps has a protrusion for interaction with the driving star; there is a circular dense groove on both lower sides of the lids;

a coupling is inserted between the chain and the bolt in the coupling between the caps, and a nut is placed on the bolt-to-cap connection.

The drum mechanism comprises a drum cylindrical body, a drum balancer, a drum pin and a drum shaft; the drum pin is connected to the drum's cylindrical body by a screw; the outer ring of the drum's cylindrical body has a threaded hole for attaching the drum balancer; a drum shaft is attached to the drum pin.

The remover mechanism consists of an extractor shaft, an extractor balancer, a extractor pin and a cylinder of the extractor; the stripper pin is threaded to the cylinder body of the stripper; the remover pin has a hole with threads for attaching the remover balance to allow the remover to be mounted; the remover shaft is housed in the cylinder of the remover;

The inner side of the cylindrical body of the remover has welded stiffening edges, and the inner construction of the cylindrical body of the remover is of symmetrical structure.

The three-roll cotton removal mechanism consists of an upper pressure roller and a lower pressure roller;

the upper pressure roller is connected to the compression spring; both the upper and lower pressure rollers are welded with two pins and a cylindrical housing, the stiffening edge is not mounted; the cylindrical body has a helical groove; the upper pressure roller is fitted with a plain bearing seat; the lower compression roller bearing housing is stationary; the bearing cap is secured with a bolt with a nut that limits the sliding range of the upper clamping roller.

The speed of the cover strip is 109.4 mm / min, and the speed of the remover is 10-60 rpm, 10-60 rpm corresponds to 0.1-0.18 mm; the distance between the receiver and the drum is 0.3-0.38 mm; the distance between the stationary covers and the drum is 0.3-0.4 mm; the distance between the drum and the movable covers is 0.22 mm or 0.3 mm; the distance between the drum and the remover is 0.1-0.18 mm; the distance between the cotton picker and the picker is 0.25-0.6 mm; distance between the removal roller and the pressure roller 0.25-0.6 mm; the distance between the lower casing and the drum is 1.5-2.5 mm and the outlet is 3-4 mm.

The invention further discloses a method of carding a carding machine carding mechanism, comprising the steps of:

the feeder feeds the cotton, and the heat strip on the surface of the receiver grabs the cotton fiber from the fed cotton during the rotation process;

after the cotton fiber is first heated through the stationary lid system, the drum mechanism allows the cotton fiber to enter the dual zone lid mechanism;

the two-zone lid mechanism has strips of front zone lids and rear zone lids; the speed of the line of the front zone caps is opposite to the direction of the speed of the drum line, and the speed directions of the rear zone caps and the drum lines coincide;

when the cotton fiber passes through the two-zone lid mechanism and is carded a second time with stationary caps, the cotton fiber is transferred to the surface of the remover; and a three-roll cotton removal mechanism removes the card from the surface of the remover.

Compared to the prior art, the advantage of the present invention lies in the fact that:

The solution of the carding system disclosed in the present description of the invention increases the effective carding area by raising the drum on the basis of the construction of a carding machine with one movable lid system; one large strip of movable lids is replaced by two small strips of movable lids (two-zone lid strip); the two small strips of movable lids rotate in opposite directions and have a decontamination inlet that effectively solves the high energy loss problem of conventional design and combines the advantages of a carding machine with a single rotary lid strip to improve the heating capacity. This design significantly reduces the load and power loss of each zone component, significantly improves discharge efficiency, significantly increases the life of the needle and the final cotton product, extends the inter-repair cycle, saves labor and material repair resources, and thus significantly increases production efficiency. Reducing the size of the cover strip solves the problem of uneven distances in conventional construction, and increases the proportion of long fibers in the cotton. Each zone has the same effect, which is equivalent to doubling the carding, dropping and draining process, and the amount of contaminants or short hairs in the final product is significantly reduced.

BRIEF DESCRIPTION OF THE DRAWINGS

The accompanying drawings, which are incorporated in and constitute a part of the invention, serve to provide a better understanding of the invention itself. Schematic examples of embodiments of the present invention and description are intended to illustrate the invention, but are not limited to the invention itself.

PAV. 1 is a general diagram of the carding mechanism of a carding machine according to the corresponding disclosed embodiments of the invention;

PAV. 2 is a schematic diagram of a forward feeder according to the respective disclosed embodiments of the invention;

PAV. 3 schematic diagram of a receiver according to the respective disclosed embodiments of the invention;

PAV. 4 is a schematic diagram of a two-zone lid mechanism according to the respective disclosed embodiments of the invention;

PAV. 5 is a schematic diagram of a drum mechanism according to the respective disclosed embodiments of the invention;

PAV. 6 is a schematic diagram of a remover according to the respective disclosed embodiments of the invention;

PAV. 7 is a schematic diagram of a pressure roller according to the corresponding disclosed embodiments of the invention;

PAV. 8 is a schematic diagram of a cotton supply roll according to the respective disclosed embodiments of the invention;

In the picture: I. front direction feeder, II. receiver, III. two-zone lid mechanism, IV. drum, V. remover, VI. three-roller removal mechanism;

1-1. cotton supply roll, I-2. pressure cylinder, I-3. first plain bearing seat;

11-1. feeder frame, II-2. feeder connector ll-3. feeder bearing socket;

111-1. Front bracket, III-2. support bracket, III-3. rear bracket, III-4. cleaning roller;

IV-1. drum cylindrical body, IV-2. drum balancer, IV-3. drum pin, IV-4. drum shaft

V-1. remover cylinder housing, V-2. remover balance, V-3. remover shaft, V-4. remover pin;

VI-1. compression spring, VI-2. upper pressure roller, VI-3. lower pressure roller, VI-4. second plain bearing seat, VI-5. cotton pick roller connector.

BEST MODES FOR IMPLEMENTATION

It should be noted that this detailed description is exemplary and is intended to describe the present invention in more detail. Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs.

It should be noted that the terms used herein are used only to describe specific embodiments of the invention, but are not intended to limit the latter examples. The singular shall be understood as including the plural unless the context clearly dictates otherwise. In addition, it is to be understood that the terms "comprising" and / or "having" used in this specification refer to the presence of the listed properties, steps, operations, elements, components and / or groups thereof.

A typical implementation of this application provides for a new carding machine heating mechanism as specified in the EIA. 1, having a forward feeder, a receiver, a drum, a two-zone lid mechanism, a remover, and a three-roll cotton removal mechanism.

In this embodiment, the following process of the carding machine carding mechanism is indicated: in particular, the forward feeder I feeds cotton to the carding machine; the heaters on the surface of the receiver II grab the cotton fiber during the rotation process; the grip of the set of heaters on the surface of the drum is stronger and the cylinder speed of the cylindrical mechanism II is higher, so that during this process the cotton fiber is transferred from the receiver to the drum; after the first carding through the strip of stationary lids, the cotton fiber is introduced into the III two-zone lid mechanism; the speed of the line of the front zone cover strip is opposite to the direction of the speed of the drum line, and the heating force is stronger; the speed of the line of the band of the end zone covers coincides with the speed of the speed of the drum, thus protecting the cotton fiber from serious damage; then the cotton fiber is carded a second time with a strip of stationary lids and transferred to the surface of the V-stripper; finally, the VI three-roll cotton removal mechanism removes the cardboard from the surface of the remover, which will be used in the further process.

In a specific embodiment of the invention, as shown in the EIA. 2, the front direction feeder I comprises a cotton feed roller 1-1, a pressure cylinder I-2, and a first plain bearing seat I-3. There is a sliding bearing seat at each end of the cotton feed roller; the pressure cylinders are located above the corresponding first plain bearing seat; there is a lock on the right side of the 1-1 cotton feed roller, and the distance between the two can be adjusted according to the material characteristics. A pin is welded to both ends of the cylindrical body of the cotton feed roller. Because the diameter of the 1-1 cotton feed roller is small, the strength meets the performance requirements, and the internal space of the cylindrical body is small, the stiffening edge is not mounted in the cylindrical body. The cotton feed roller has grooves 3 mm deep, 8 mm apart and 5 mm wide, which improve the grip of the cotton. The two ends of the pin have grooves so that the cotton flowing in the feed line is wrapped around both ends of the pin instead of being wrapped around the pin shaft at both ends of the cotton feed roller. The compression cylinder I-2 is fitted with a spring and the piston at the lower end contacts the first plain bearing seat I-3. The pressure of the first sliding seat I-3 can be adjusted by a spring by turning the rear cover of the upper part of the pressure cylinder with a wrench. By adjusting the pressure, it is possible to maintain a constant thickness of the fed cotton layer and to protect the heat sink from damage when the cotton pile accumulates or the cotton layer is too thick, a roller bearing is placed in the middle of the first plain bearing seat I-3 -down; the roller bearing is mounted on the left short shaft and the right short shaft; the two short shafts are threaded to each other and there is a short shaft reinforcing bar on the right side of the short shafts; the lowest position of the plain bearing is limited by the bolt and nut under the plain bearing seat.

In a specific embodiment of the invention, as shown in the EIA. 3, the receiver II has a receiver frame 11-1, a receiver connector II-2, and a receiver bearing socket II-3. The receiver connector II-2 is welded to the two pins and the receiver's cylindrical body and has no stiffening edge. A 2 mm deep, 2 mm wide groove is formed at a distance of 25 mm from the left and right edges of the receiver connector II-2 to make it easier for the worker to press and secure one end of the heat set when wrapping the heat set. A groove for the sealing ring is formed at the left and right ends of the pins.

As shown in the EIA. 4, one zone of the two-zone lid mechanism is supported on three components, i.e., the front bracket 111-1, the support bracket III-2, and the rear bracket II1-3, which provide stability during operation. The cover strip is mounted from the covers; the lids are fitted with a set of heaters which is fixed in a clamping slot on both sides. The shape of the assembled cover block mimics a chain drive. On the inside of the caps there is a protrusion for interaction with the driving star. There is a circular dense groove on both undersides of the lids, which, when the star rests on it, facilitates its movement. A coupling is inserted in the coupling between the chain and the bolt, which simulates a friction in the chain drive to reduce friction. When the cover area is divided into two parts, 72 covers are installed in each area. With such a design, the working angle of each zone is significantly reduced compared to the original zone; each zone has a two-stage cleaning roller III-4 in the strip of movable covers, which increases the number of cleanings compared to the original design. Therefore, with this construction, the situation where the lid becomes clogged is substantially changed, thus improving the heating capacity of the machine and extending the service life of the lid strip heater set. Two cleanings improve the machine’s decontamination capacity. At the same time, the shortening of the length of each zone improves the plane of the lid strip, as well as significantly improves the accuracy of the height of each lid compared to the conventional design.

As shown in the EIA. 5, the drum mechanism has a drum cylindrical body IV1, a drum balance IV-2, a drum pin IV-3, and a drum shaft IV-4. This is an important part of the heating system. The drum pin is connected to the drum's cylindrical body with a screw, and the radial beat of the drum must not exceed 0.02 mm to ensure a good heating result. Therefore, the outer ring IV-1 of the drum cylindrical body has a threaded hole for attaching the drum balancer IV-2. After assembly work, the dynamic balance must be checked at 400 rpm. and the total weight of the drum balancer V-2 must not exceed 15 kg in order to reduce the moment of inertia of the machine during operation.

As shown in the EIA. 6, the remover mechanism has a remover cylinder housing V-1, a remover balance V-2, a remover shaft V-3 and a remover pin V-4. The remover pin is attached to the remover cylinder housing with a screw. Like the drum, the radial beat of the remover must also be limited to 0.02 mm. Therefore, a threaded hole is left in the remover pin V-4 to attach the remover balance. To ensure operating accuracy, the internal construction of the remover is symmetrical. Because the construction diameter is 698 mm to ensure the strength and accuracy of the remover cylindrical body V-1, four 8 mm thick stiffening edges are welded inside the remover cylindrical body V-1 and the stiffening edges are 175 mm apart. After assembly work, the dynamic balance must be checked at 400 rpm. and the total weight of the remover balancer V-2 must not exceed 15 kg in order to reduce the moment of inertia of the machine during operation.

As shown in the EIA. 7 and EIA. 8, the three-roll cotton removal mechanism comprises a VI-1 compression spring, a VI-2 upper compression roller, a VI-3 lower compression roller, a VI-4 second plain bearing seat, and a VI-5 cotton removal roller connector. The upper compression roller VI-2 is connected to the compression spring VI-1, and the second plain bearing seat VI-4, like the feed mechanism, provides maximum protection for the machine when cotton accumulates in the pile. The upper and lower pressure rollers are welded to the two pins and the cylindrical housing and do not have a stiffening edge. Spiral grooves 5 mm wide and 2 mm deep are carved on the surface of the cylindrical body to improve the grip of the card and to stabilize the air flow. Number of helical grooves 50. The lower compression shaft VI-3 bearing housing is a stationary bearing housing; the bearing cap is secured with a bolt with a nut that limits the sliding range of the upper pressure roller VI-2.

About the design speed of the two-zone lids:

According to the experiment, there are two indicators for measuring the result of the final product: the first indicator is the amount of medium and long cotton, and the second is the amount of long cotton.

When cotton is wrapped on a cover strip, the second indicator is in the range of 22.1% to 47.7%, and the speed of the covers has a significant effect on the second indicator. At an interval of 149-449 mm / min, the increase in speed also increases the second indicator; and at a range of 449-849 mm / min, the second indicator is relatively stable, and also stable at 40%. At a speed of 949 mm / min, the second indicator is the max. 47.7%.

The second indicator is in the range of 10.1% -17.5%; speed in the range of 149-349 mm / min, and as the speed increases, the first indicator will rise. At an interval of 449-849 mm / min, the speed increases gradually and the first indicator remains relatively stable, at about 15.9%. At a speed of 949 mm / min, the second indicator drops to 13.9%. The higher the speed of the cover strip, the higher the first and second indicators. Therefore, a speed of 450 mm / min or less is more appropriate to ensure high performance and product quality.

The cap band speed formula is

100 1x1 19 29 v = 7.95 f — X ¢ -or—) xl4x36.5 = 5.1 /or2.188 f

180 26x26 29 19 where it is determined that f - 50 Hz and the value is inserted into the formula to obtain v = 5.1 x 50 = 255 mm / min or 2.188 χ 50 = 109.4 mm / min where, the front cover strip and the drum rotate in opposite directions. directions so that the cotton can be carded several times in a single process, and the relative speed difference in this zone is large in order to achieve the intended improvement in carding capacity. The end cap strip and drum rotate in the same direction, which can completely improve the removal efficiency. Once the fiber has been effectively heated to prevent serious damage to the fiber, the back strip of the covers should rotate forward.

About pickup speed selection:

According to the experiment, there are five indicators: the first indicator is 5% long cotton, the second indicator is 3% long cotton, the third indicator is short cotton content, the fourth indicator is medium and short cotton content, and the fifth indicator is medium and long cotton content. .

According to the first indicator, based on the results of the experiment, the best result is 27.82 mm at 24.9 rpm, followed by the results at 19 mm / min and 29 mm / min. Based on the effective length of the first indicator, based on the results of the experiment, the best result is 22.54 mm at 24.9 rpm, followed by the results at 19 mm / min and 29 mm / min. Considering the amount of short hairs in the first indicator, based on the results of the experiment, the best result is 27.1% at 19 rpm, followed by the results at 29 mm / min and 39 mm / min. Thus, it can be concluded that the best result is achieved at 19 rpm. speed.

According to the second indicator, based on the results of the experiment, the highest volume level is reached at 19 rpm, followed by the results at 29 mm / min and 24 mm / min. This indicates that the result of the second indicator is better at 19 rpm than at 29 rpm. Thus, it can be concluded that the best result is achieved at 19 rpm. speed.

According to the third indicator, based on the results of the experiment, the highest level is reached at 24 rpm, followed by the results at 19 mm / min and 29 mm / min, which are 1.89% and 1.59% higher than the control data. This indicates that the effect of the second indicator is better at 19 rpm than at 29 rpm. Thus, it can be concluded that the best result is achieved at 24 rpm. speed.

According to the fourth indicator, based on the results of the experiment, the highest level is reached at 24 rpm, followed by the results at 29 mm / min and 19 mm / min, which are 8.63% and 3.53% higher than the control data. Thus, it can be concluded that the best result is achieved at 24 rpm. speed.

According to the fifth indicator, based on the results of the experiment, the highest level is reached at 19 rpm, followed by the results at 24 mm / min and 19 mm / min, which are 10.39% and 0.49% higher than the control data. Thus, it can be concluded that the best result is achieved at 29 rpm. speed.

In summary, 10-60 rpm must be selected. remover speed.

About the selection of the gap width of the supply part

The distance from the cotton feed roller and the receiver to the cotton feed plate is from 0.1 mm to 0.23 mm, which increases with increasing thickness of the fed cotton. According to the latest research, when the output of the carding machine exceeds 30 kg / h, the distance of the cotton feed roller should be about 0.15 mm. When the machine is fitted with a needle bar type design and the value of b is 24, the final product shows a more obvious result of fiber protection than other structural rollers under the same conditions; also, in a particular machine with low-quality rotary spinning yarns (where lower requirements for short hair content, i.e. than the overall production level), the distance can be extended accordingly to reduce unnecessary industrial costs. However, when the performance of the machine is high, the distance selection range must also be extended.

In summary, the distance was found to be between 0.1 mm and 0.18 mm.

About selecting the distance between the receiver and the drum:

Based on many years of experience, the gap between the drum and the receiver is usually 0.8 mm. With a large gap, cotton sliding back and forth between the two parts can be improperly moved or even severely damaged.

The receiver speed of the latest machine is high (1111 rpm to 2224 rpm), which means that the machine's performance is high (approximately 1500 rpm for 98 kg / h processed wool). In this case, the material wound on the surface of the roll is smoothly transferred to the drum under a strong centrifugal force, and the phenomenon of congestion does not occur so easily. The most commonly used maximum receiver speed is now between 590 rpm and 1040 rpm.

The beam is subjected to centrifugal force at high speed. In addition, since the weight of the roller structure is high, the effect of centrifugal force cannot be ignored. The drum and receiver will expand outward at high speeds, so the gap is actually smaller than in the original design. Therefore, the use of excess speed is not easy.

The working width of the machine is 1020 mm. When the roller heater sets are mounted at the rear, it is difficult to ensure the cylindrical nature of the surface. This means that the actual distance may be uneven. There must also be a larger gap to avoid a collision.

In summary, the distance was found to be between 0.3 mm and 0.38 mm.

About selecting the distance between the stationary cover strip and the drum:

Based on many years of application experience, too small a gap can cause significant damage to the fiber. So to protect the cotton, the gap here needs to be a little bigger. Fully stretched cotton on the surface of the receiver is thin. Therefore, as the capacity increases, the distance must also be increased here so that the cotton is not damaged and the use of the raw material is increased.

In summary, the distance here is between 0.3 mm and 0.4 mm.

About selecting the distance between the drum and the moving cover strip:

Based on many years of experience, the gap between the strip of movable lids and the drum is always 0.2-0.3 mm (0.7-0.9 mm at the inlet and outlet). However, the findings from data monitoring alone are not accurate, so the effects of increased power need to be addressed. Thus, it is determined that the distance can be increased. In this curved carding area, the flexibility of the lids and drum results in a hot fiber, and after operations with the fiber such as carding and transfer, the cotton fiber acquires a certain degree of directivity. Thus, to improve the carding action, the gap here can be reduced accordingly.

In summary, a distance of 0.22 mm or 0.3 mm (0.18 mm or 0.25 mm at the input and output) is selected here.

About choosing other distances:

As the remaining distances have little effect on the product result and the parameters used in previous years are relatively stable, it was decided to use the previous parameters in the machine. Accordingly: the distance between the drum and the remover is 0.ΙΟ. 18 mm; the gap between the cotton picker and the picker is 0.25-0.6 mm; the gap between the cotton pick-up roller and the receiver is 0.25-0.6 mm; the distance between the lower cover and the drum is 1.5-2.5 mm, and the distance at the inlet is 3-4 mm.

Check calculation for remover component bearing:

The extractor weighs 106.5 kg and has a speed of 10-60 rpm (60 rpm is the maximum design speed); the belt drive support neck pressure is 607 N; the radial load of the cotton for the remover is about 350 N and the axial load of the remover is about 120 N. The diameter of the connection between the shaft and the bearing is 50 mm. It was decided to use a self-aligning ball bearing to ensure a radial impact of less than 0.02 mm during rotation of the remover.

Under this condition, the radial bearing load is

106.5 * 9.8 + 350 + 650 '2

The axial load of the bearing is ^ » ^{= 120ΛΓ} , and the default service life is 4 = 8x300x8 = 19200 / z

Calculation of the coefficient £

F _r

120

1000.35 = 0.119

Therefore, a self-aligning ball bearing with code 1210, inner diameter 50 mm, outer diameter 90 mm, and width 20 mm, ^{e = 0} · ² , C _o = 22 is used. & N

F

-2- <e

Therefore, ^Fr

Preliminary calculation of equivalent dynamic load

According to the formula

P _r = F _r + Y'F _a = 1000.35 + 3.1x120 = 1372.35 #

Calculation of bearing life

10 ⁶

60 » ^v P _r

10 ⁶ 22800

60x60 1372.35) ³ h = 1.69x10 ⁶ A> Ą '

This means that the actual service life is much longer than the design requirement, so the bearing is suitable.

About the design control calculation of the remover shaft:

It is known that the input power of the take-off shaft is P = 2.2kW _{t 0} speed «= 60r / min according to 3.1, the pressure of the belt drive support pin is 607 N, and the weight of the pick-up is 106.5 kg.

The torque of the remover shaft can be calculated

9550P n

9550x2.2x1000 = 350166 # twm

The minimum shaft diameter can be calculated in mm = 112x = 35.15mm

Taking into account the wedge groove j, the diameter is increased by 10%, then d = (1 + 10%) x 35.15 = 38.665mm

It was found that ^d = 45mw

One end of the shaft is connected to the pulley by a wedge pin and the diameter here is at least 45 mm. At the other end of the shaft is an M10 10 mm deep threaded blind hole for mounting the retaining ring. The bearing point is fixed by the shaft arm and the other end is fixed by the bearing mounting ring; here the shaft diameter is 50 mm, and both are compatible with k6. A pin must be fitted to the shaft; here h6 is used for alignment and the shaft diameter is 65 mm. To save machining costs, the diameter of the middle shaft part is reduced by 1 mm to 64 mm and the surface is only roughened. Both bearing ends are equally attached and will not be characterized further.

The length of each shaft segment is then determined:

Segment I-II: = 45m / «, £ _IU = 155mm, wedge groove shaft size 14 x 50;

Segment II-III: <ήΐ4ΐι = ⁵ 0ww, 4 _wn = 30mm mounting ring mounting groove is 1.5 mm deep;

Segment III-IV: ⁼ 65ww, Z _m . _Į = 120mm.

Segment IV and V ^ 64 ^ -7 = ^ = ^^ 86011101 _{urkšt fodder} to the _NLF.

Segment V-VI: = 65 ^, ^ = 120mm.

Segment VI-VII ^ vi vii 5Qmm ^_ L _VLV]] -30mm un _v jrtinimo ring mounting groove is 1.5 mm deep;

Segment VII-VIII: ^ νπ-vm = 45 ^, 1 ^,. ^ = 110mm

It can be seen from the figure that the dangerous part is Part II. The maximum bending moment is M ~ 62Χ2Α5Νιη _t q The torque is T = 350.166JV m

The tension formula is “V W 2W W

The mouse moment of circular cross-section is ^ = ^ (1 r) -o.id ³ (i / J ⁴ b = 7

In the formula, the value is changed to obtain a stress of 7.9 MPa. The shaft is made of 45 steel and treated by hardening. According to the relevant data, the allowable stress is 60 MPa lower than the calculated stress, so the shaft strength is sufficient.

Drum Component Bearing Check Calculation:

Drum weight 210 kg and speed 403 rpm; the belt drive support neck pressure is 1100 N; the radial load of the cotton on the drum is about 350 N and the axial load of the drum is about 120 N. The diameter of the connecting part between the shaft and the bearing is 80 mm. In order to ensure a radial stroke of less than 0.02 mm during the rotation of the drum, it was decided to use a self-aligning ball bearing.

Under this condition, the radial bearing load is

210x9.8 + 350 + 1100

F = --------------- = 1754 # ^r 2 a λ ą r

The axial load of the bearing is ~ ^υ and the default service life is

4 = 8x300x8 = 19200/1

1. Calculation of the coefficient

Therefore, a self-aligning ball bearing with code 1216, inner diameter 80 mm, outer diameter 140 mm, and width 26 mm, ^{e = 0} · ¹⁸ , C ₀ = 39.5 £ # is used.

4 _<f?

Therefore, ^Fr

2. Preliminary calculation of equivalent dynamic load

According to the formula

P _r = F _r + Y _} F _O = 1754 + 3.6x120 = 2186 #

3. Calculation of bearing life

10 ⁶ C _{o F}

10 ⁶ 39500

60x60 ⁽ 2186) ³ h = 1.32x10 ⁶ /?> 4 '

This means that the actual service life is much longer than the design requirement, so the bearing is suitable.

About the design control calculation of the drum shaft:

It is known that the input power of the drum shaft is ^{p =} ^ kW. ₀ speed ^{n =} 403r / min. According to 3.1, the belt drive support neck pressure is 1100 N and the drum weight is 210 kg.

Drum shaft torque can be calculated

9550P n

9550x4x1000

397 = 96211.7jV-mm

The minimum shaft diameter can be calculated

[p Γ ~ 4 ~ d> C \ - mm = 112xJ -65A5mm

V n V 397

Taking into account the wedge groove j, the diameter is increased by 10%, then the size of the support neck is if = (l + 10%) x35.15 = 38.665mm

It was found that d =

One end of the shaft is connected to the pulley by a wedge pin and the diameter here is at least 45 mm. At the other end of the shaft is a M10 10 mm deep threaded blind hole for mounting a speed sensor. The bearing point is fixed by the shaft arm and the other end is fixed by the bearing mounting ring; here the shaft diameter is 50 mm, and both are compatible with k6. A pin must be fitted to the shaft; here h6 is used for alignment and the shaft diameter is 65 mm. To save machining costs, the diameter of the middle shaft part is reduced by 1 mm to 64 mm and the surface is only roughened. Both bearing ends are equally attached and will not be characterized further.

The length of each shaft segment is then determined:

Segment I-II: = 60 ™™,! ^ = 155πΗη ₍ size of the draw groove in the shaft 14

X 50;

Segment II-III: ^ n-m “-SOmm ^ mounting ring mounting groove is 1.5 mm deep;

Segment III-IV: ^ ^{m iv =} ~ 120mm.

Segment IV-V: ^{c /} ' ^v ~ ^v “ ^{86 ! / Ί!} · 4'.ν ~ 860mm _{tjk pa} roughened;

Segment V-VI: ^ ^{V VI} “- 120mm.

Segment VI-VII: ^ ^V!] “ ^30mm , the mounting groove of the mounting ring is 1.5 mm deep;

Segment VII-VIII: ^ vn-vni ⁼ 65mm, Ι ^ η- ™ ⁼ 80mm

It can be seen that the dangerous part is Part II. The maximum bending moment is ^ = 62.8245iV-m _{and the} torque = 350.166AT-m The stress formula is and

The polar moment of circular cross section is w ~ (ip ⁴ ) -o.id ³ (ip ⁴ ), p = ^ 32 d

In the formula, the value is changed to obtain a stress of 11.7 MPa. The shaft is made of 45 steel and treated by hardening. According to the relevant data, the allowable stress is 60 MPa lower than the calculated stress, so the shaft strength is sufficient.

About checking the drum roller deflection:

This is a necessary prerequisite for maintaining a stable drum distance when interacting with other heating components. However, drum factors such as dynamic imbalance, shape distortion, and heat gauge pressure will affect the distance, and at the same time will affect the fiber layer displacement and the heating result. Therefore, it is necessary to check the stiffness of the roll. A pin is installed on both sides of the drum roll, which is connected by a conical shaft coupling and a shaft; the roll is fitted with a row of edge plates to improve the stiffness of the roll.

The coiled heat set pressure q acting on the surface of the roll is calculated according to the formula

P ^q br ₀

P is the tension of the coiled heat set, which is 80 N; b - thickness of the base of the hot set, which is 0.8 mm; ^r ° is the outer radius of the drum roll, which 2 is 615 mm, then q = 0.162 N / ^{2 5} .

Under the action of q, the roll part undergoes a radial shrinkage deformation, so a one-unit-width axial strip is removed from the roll to examine the radial deflection curve under the heat set pressure q, the pin and the roll support inner circle to obtain a concave roll deformation.

Suppose y is the radial displacement on the axial specimen, which is the distance by which the radius of the circle corresponding to the cross-section is shortened, and the circumferential pressure of the circle is F, then

Ey

F = r where: E is the modulus of elasticity of the drum roll material, which is ^12xl ° ^{5 mm2} ;

r is the mean radius of the roll, mm.

Suppose the compressive stress along the unit length of the two sides of the sample strip is equal to T, then _τ Ehy r where: h is the wall thickness of the roll, which is 10 mm.

Since = ¹ , the representative force R of T is directed outwards along a radius of formula:

r

R is directly proportional to the deflection y and is distributed over the strip of the specimen, so the latter can be considered as an elastic base beam. Since the strip of sample is not alone, a bypass strip will be attached to it; thus the formula for the bending stiffness of the strip is:

D = ^Eh \ η (\ - μ ² ) where: P- Poisson's ratio, which is 0.31.

Then £> = ¹ · ^{8 x} 10 ⁷ jV · wot.

The right direction of the X axis of the coordinate system is a positive direction, the downward direction of the Y axis is a positive direction, the downward direction of the load q is a positive direction, the downward direction of the bend y is a positive direction, the direction of rotation ^θ clockwise is a positive direction, the shear force is Q k the left part of the test strip is in the positive direction and the direction of the bending moment M is counterclockwise in the positive direction.

According to the formula of material mechanics, d ⁴ y Eh

D — to- = q --- y dx ⁴ r ²

Suppose

Λ ⁴ = ^Eh = 1 ^1- ^ ^{2 P} ADr ¹ _r 2 _h 2

Thus ^ = 0.0164 _{a = +} A ₌ λ ^ & ₊ (^ ^ų Eh dx r ¹ r ² 'β * dx ^Ą r *> r ¹

Judging by

Eh y = C ^ h {px) sin (/? X) + C ^ sKfix} cos (/? X) + C ^ ch {px) sin (/? X) + C ^ ch (px) cos (/? x) + q

The formula for calculating the deflection is qr ² _γ _ _{ν (} β. In sh (J3l) -sin (^ Z) V ₂ (βχ) ch (fi) -cos (/ 3Z) K ₃ (βχ) sfc (;? Z) + s _in (/ 7 /) 2β ² sA (/? /) + sin (/? Z) β sh (fll) - sin (/? Z) where, ¹ is the length of the sample strip, which is 1220 mm; ^ (^ 0+ ^sin W j _r cos (/? Z) - cos (/? Z) sh (J%) + sin (/? /) Y _ra , then ^y Eh ¹ 2β ² β

After setting the value, v = 8.] 4xl0 - '' [l- _t '°° ^164jc (sin0.0164x cos0.0164x)] = 0.015mm <0.02mm

In summary, stiffness is adequate.

About the control analysis of the drum roll:

Finite element analysis of the drum roll is performed by unigraf NX (UG). stiffness edges are separated by 110 mm; the wall thickness of the roll is 10 mm; drum speed 360 rpm and diameter 1284 mm, length 1220 mm. The distribution of stress and strain can be obtained by analysis. PAV. 3-8 shows the distribution of individual drum deformations. It can be seen that the deformation of the entire drum is severe and uneven, which is likely to lead to unevenness in distance. Before optimizing the structure, it can be noticed that the amount of strain deformations is high, so it was decided to increase the length of the stiffness edges of the gasket. After structural optimization of the stiffness edge, the deformation distribution is more even, which is conducive to maintaining equal gaps. The result shows that the maximum deformation is 0.002472 mm <0.02 mm, which means that the drum roll design meets the requirements for use.

Receiver bearing control calculations

The receiver weighs 51.6 kg and has a speed of 1039 rpm; the belt drive support neck pressure is 450 N; the radial load of the cotton on the receiver is about 460 N and the axial load of the drum is about 90 N. The diameter of the connecting part between the shaft and the bearing is 35 mm. To ensure a radial stroke of less than 0.02 mm during rotation of the receiver, it was decided to use a self-aligning ball bearing.

Under this condition, the radial bearing load is

51.6x9.8 + 460 + 450

F _r = ------------------ = 707.84; V

Axial bearing load is ^ ₀ default service life is 4 = 8x300x8 = 19200/1

1. Calculation of the coefficient

F 90 - ------- 0 127

F 707.84

Therefore, a self-aligning ball bearing with code 1207, inner diameter 35 mm, outer diameter 72 mm and width 17 mm, ^{e = 0} · ²³ , C ₀ = 15.8jW is used

Therefore,

2. Preliminary calculation of equivalent dynamic load

According to the formula

P _r = F _r + T /; = 707.84 + 2.7 ^x 90 = 950.847V

3. Calculation of bearing life

10 ⁶ c _{0 f} l -—r — i - ^h Wn ^{ P,

10 ⁶ 15800

60x60 950.84) ³ h = 2.12χ10 ⁶ Λ> 4 '

T.y. the actual service life is much longer than the design requirement, so the bearing is suitable.

3. 8 Cotton Harvesting Roller Bearing Control Calculations

Cotton unloading roller weight 42 kg, receiver speed 296 rpm; the belt drive support neck pressure is 220 N; the radial load of the cotton on the receiver is about 300 N and the axial load of the drum is about 55 N. The diameter of the connecting part between the shaft and the bearing is 30 mm. To ensure a radial stroke of less than 0.02 mm during rotation of the receiver, it was decided to use a self-aligning ball bearing.

Under this condition, the radial bearing load is

42x9.8 + 220 + 300

F _r ------------------ = 465.8 / 7

Axial bearing load is ₀ Default service life is = 8x300x8 = 19200A

1. Calculation of the coefficient

Therefore, a self-aligning ball bearing with code 1206, inner diameter 30 mm, outer diameter 62 mm and width 16 mm, ^{e = 0} · ²⁴ , C _o = 15.8 £ / 7 is used

Therefore, ^Fr

2. Preliminary calculation of equivalent dynamic load

According to the formula

P _r = F _r + Y _x F _a = 465.8 + 2.7x55 = 613.477

3. Calculation of bearing life

10 ⁶ c - (- y = 60 « ^v P _r '

10 ⁶ 15800

60x60 613.4) ³ h = 1.57x10 ⁶ h> L _ii

T.y. the actual service life is much longer than the design requirement, so the bearing is suitable.

The foregoing is merely illustrative of the most suitable embodiments of the present invention and is not intended to limit the present invention, and various changes and modifications may be made by those skilled in the art. Any modifications, equivalent modifications, improvements, etc., made in accordance with the spirit and scope of the present invention, are intended to be included within the scope of the present invention.

Claims (10)

DEFINITION OF THE INVENTION 1. A carding machine carding machine comprising: a feeder, a receiver, a cylindrical mechanism, a two-zone lid mechanism, a remover and a three-roll cotton removal mechanism, characterized in that: the feeder has a cotton feed roller that is used to pick up the cotton; the surface of the receiver is adapted to the set of heaters, the heaters on the cotton supply roll are in contact with the cotton and grab the cotton fiber from the fed cotton during the rotation process; after the cotton fiber is first carded through the stationary cap system, the cylindrical mechanism allows the cotton fiber to enter the dual zone cap mechanism; the dual zone lid mechanism consists of front zone caps and rear zone caps; the speed line of the front zone caps is opposite to the direction of the cylinder speed line and the directions of the rear zone and cylinder speed lines coincide; when the cotton fiber passes through the mechanism of the two-zone lids and is carded a second time with stationary lids, the cotton fiber is transferred to the surface of the remover, the surface of the remover being adapted to the set of heaters; the surface of the three-roll cotton peeling mechanism contacts the groove and removes the card from the peeling surface. 2. A carding machine carding mechanism according to claim 1, characterized in that the forward feeder has a cotton feed roller, a pressure cylinder and a plain bearing seat; a sliding bearing housing is mounted at each end of the cotton feed roller, and each sliding bearing housing has a pressure cylinder; a latch is mounted on one side of the cotton feed roll and the distance between the cotton feed roll and the latch is adjustable according to the characteristics of the material; a pin is welded to both ends of the cylindrical body of the cotton roll and the stiffening edge is not mounted in the cylindrical body of the cotton roll; there is a groove in the cylindrical body of the cotton supply roll; there is a groove at both ends of the pin; the pressure cylinder is fitted with a spring; the piston in the lower part of the pressure cylinder is in contact with the corresponding plain bearing seat; the rear cover of the upper part of the pressure cylinder is rotated to compress the spring and thus adjust the pressure of the plain bearing seat. 3. The carding mechanism of a carding machine according to claim 2, characterized in that a roller bearing is inserted in the middle of the plain bearing seat; the roller bearing is mounted on the left short shaft and the right short shaft; the two short shafts are threaded to each other and there is a short shaft reinforcing bar on the right side of the short shafts; the lowest position of the floating plain bearing is limited by a bolt and nut under the plain bearing seat. 4. The carding mechanism of a carding machine according to claim 1, characterized in that the receiver has a receiver frame, a receiver connecting element and a receiver bearing socket; the receiver connector is welded to the two pins and the receiver cylindrical body, and the stiffening edge is not mounted in the receiver cylindrical body; there is a bearing socket at each end of the receiver connector and a receiver frame mounted on the bearing socket; a groove is formed at a distance from the left and right edges of the receiver connecting member for pressing and securing one end of the heater set; there is a groove in the sealing ring at the left and right ends of the pins. 5. The carding mechanism of the carding machine according to claim 1, characterized in that the area of the covers of the two-zone lid mechanism is divided into two parts, and a chain of lids is provided in each zone; each zone has a two-stage cleaning roller in the strip of movable lids; each zone is supported by three support elements, i. front bracket, support bracket and rear bracket; the lids are fitted with a set of heaters which is fixed in a clamping slot on both sides; the inner side of the caps has a protrusion for interaction with the driving star; there is a circular arcuate groove on both lower sides of the lids; a coupling is inserted between the chain and the bolt in the coupling between the caps, and a nut is placed on the bolt-to-cap connection. 6. A carding machine carding mechanism according to claim 1, characterized in that the drum mechanism comprises a drum cylindrical body, a drum balancer, a drum pin and a drum shaft; the drum pin is connected to the drum static body by a screw; the outer ring of the drum's cylindrical body has a threaded hole for attaching the drum balancer; there is a drum shaft in the drum pin. 7. The carding mechanism of the carding machine according to claim 1, characterized in that the detachment mechanism comprises a detachment shaft, a detachment balancer, a detachment pin and a detachable cylindrical housing; the stripper pin is threaded to the cylinder body of the stripper; the remover pin has a hole with threads for attaching the remover balance to allow the remover to be mounted; the remover shaft is housed in the cylinder of the remover; the inner side of the cylindrical body of the remover is welded with a series of stiffening edges, and the inner structure of the cylindrical body of the remover is of symmetrical structure. 8. The carding mechanism of the carding machine according to claim 1, characterized in that the three-roll cotton removal mechanism has an upper pressure roller and a lower pressure roller; the upper pressure roller is connected to the compression spring; both the upper and lower pressure rollers are welded with two pins and a cylindrical housing, the stiffening edge is not mounted; the cylindrical body has a helical groove; the upper pressure roller is fitted with a plain bearing seat; the lower compression roller bearing housing is stationary; the bearing cap is secured with a bolt with a nut that limits the sliding range of the upper clamping roller. 9. The carding mechanism of the carding machine according to claim 1, characterized in that the speed of the cover strip is 109.4 mm / min and the speed of the remover is 10-60 rpm, 10-60 rpm corresponds to 0.1-0.18 mm; the distance between the receiver and the drum is 0.3-0.38 mm; the distance between the stationary covers and the drum is 0.3-0.4 mm; the distance between the drum and the strip of movable lids is 0.22 mm or 0.3 mm; the distance between the drum and the remover is 0.1-0.18 mm; the distance between the cotton picker and the picker is 0.25-0.6 mm; distance between the cotton removal roller and the pressure roller 0.25-0.6 mm; the distance between the lower casing and the drum is 1.52.5 mm and the outlet is 3-4 mm. A method of heating a heating mechanism of a heating machine according to claims 1-9, comprising: a feeder that feeds cotton, and a heat strip on the surface of the receiver grips the cotton fiber from the fed cotton during the rotation process; characterized in that after the cotton fiber is first carded through a system of stationary lids, the cylindrical mechanism allows the cotton fiber to enter the two-zone lids mechanism; the dual zone lid mechanism consists of front zone caps and rear zone caps; the speed line of the front zone caps is opposite to the direction of the cylinder speed line and the directions of the rear zone and cylinder speed lines coincide; when the cotton fiber passes through the two-zone lid mechanism and is carded a second time with stationary caps, the cotton fiber is transferred to the surface of the remover; and a three-roll cotton removal mechanism removes the card from the surface of the remover.