JP5526531B2 - Spinning cooling device and melt spinning method - Google Patents

Description

  The present invention relates to a spinning cooling device and a melt spinning method.

  Conventionally, in the production of multifilament yarns, various researches and developments have been made on the method of stably cooling the thermoplastic polymer discharged from the spinneret. It has been implemented. As a general cooling device, there is an internal blow cooling device that blows an air flow inward from the outside of a yarn traveling path to a yarn discharged from a spinneret having spinning holes arranged in an annular shape. In addition, there is a cooling device that improves the quality of yarn properties and improves the productivity of yarn by using the inner blow cooling device while actively heating the atmosphere directly under the base.

  For example, Patent Document 1 discloses a melt spinning cooling device as shown in FIG. FIG. 15 is a schematic longitudinal sectional view of the spinning annular cooling device of Patent Document 1. As shown in FIG. In the figure, 1 is a spinneret, 4 is a converging guide, 22 is a yarn, 43 is a cooling cylinder, and 44 is a heating cylinder. Hereinafter, in each drawing, when a member corresponding to the already-explained drawing exists, the description may be omitted by using the same reference numerals. Patent Document 1 is composed of two upper and lower cooling cylinders 43 and a heating cylinder 44, which cools the yarn 22 spun by the cooling cylinder 43 on the side close to the spinneret 1 surface and heats the heating cylinder 44 near the outlet side. Has proposed a heat treatment apparatus for melt spinning that performs two-stage heat treatment for tempering the yarn 22 by the above method. When this method is used, the spun yarn 22 is quenched with a cooling air flow and then subjected to a tempering operation using a heating air flow, thereby removing the molecular orientation distortion of the yarn due to the rapid cooling. It is described that the mechanical strength of the strip can be improved and the quality can be made uniform.

  However, according to the knowledge of the present inventors, even if the tempering operation using the heating airflow is appropriately performed after quenching with the cooling airflow, circumferential air temperature spots are present in the heating airflow. For example, a difference in molecular orientation strain occurs between the yarns. In particular, according to the knowledge of the present inventors, the heating cylinder 44 is a mechanism for supplying a heating airflow from below and exhausting from the upper side opposite to the supply side. On the other hand, in the heating cylinder 44, the accompanying flow caused by the yarn flows downward from above, so that the heating airflow and the accompanying flow collide, and temperature spots are generated due to airflow turbulence. It may get worse. Therefore, the configuration described in the specification for the heating airflow flowing into the heating cylinder 44 may not be sufficient to obtain circumferential air temperature uniformity.

  Further, Patent Document 2 discloses a spinning cooling device as shown in FIG. FIG. 9 is a schematic longitudinal sectional view of the spinning annular cooling device of Patent Document 2. In the figure, 2 is a cooling air spraying device, 3 is a hot air spraying device, 8 is a rectifying filter, and 22 is a yarn. This spinning cooling device is composed of a two-stage airflow spraying device. Patent Document 2 discloses a specific air volume in an area within 10 cm immediately below the spinneret 1 according to the take-up speed (m / min) of the yarn 22 spun from the spinneret 1 and the number of yarns (lines) (NL / min), and a method for producing an ultrafine fiber that blows an airflow having a specific air temperature range in the yarn traveling direction has been proposed. Further, the document discloses that the amount of air blown from the hot air blowing device 3 in the upper stage is smaller than the amount of air discharged from the cooling air blowing device 2 in the lower stage and the discharge air temperature of the hot air blowing device 3 is cooled. There has been proposed a method for producing ultrafine fibers that is higher than the discharge air temperature of the air blowing device 2. When these methods are used, the temperature of the inside and outside of the yarn 22 discharged from the cap hole 23 is made uniform, so that the yarn cooling is made uniform, and the tension difference and the accompanying flow difference generated between the yarns are reduced. It is described that, as a result, yarn breakage can be suppressed, and further, occurrence of fusion and draw resonance due to yarn swinging can be suppressed. Furthermore, it is described that, by forming a specific air temperature distribution in the yarn traveling direction, it is possible to manufacture high-quality ultrafine fibers by performing appropriate cooling while suppressing rapid thinning deformation. ing.

However, according to the knowledge of the present inventors, the method described in the specification of Patent Document 2 defines the arrangement of the nozzle holes 23 as a means for equalizing the atmospheric temperature inside and outside the yarn 22. In addition, the atmospheric temperature distribution is only defined in the yarn traveling direction, and even if hot air is blown as described in the specification, the air flow blown out from the hot air blowing device 3 is When the circumferential temperature difference occurs, a tension difference and an accompanying flow difference occur between the yarns in the circumferential direction, and eventually the yarn physical properties may be deteriorated by fusing due to yarn breakage and yarn sway.
In the specification of this document, the ambient temperature immediately below the spinneret 1 is described, but the uniform high air temperature air supply means, the heat retaining means, and the blowing means are not specified. Further, in the examples, the temperature fluctuation at a certain measurement point is described as ± 1 ° C., but this is a temperature fluctuation value at one point in the yarn traveling direction, and the wind temperature in the circumferential direction is not described in the specification. Not listed.

  A spinning cooling device having an apparatus configuration similar to that of Patent Document 2 is disclosed in Patent Document 3. In this document, as shown in FIG. 9, a hot air spraying device 3 and a cooling air spraying device 2 are provided continuously from directly below the spinneret 1, and the single yarn fineness (denier) from the spinneret 1 toward the yarn running direction. Alternatively, according to dtex), a fiber manufacturing method in which the ambient temperature T (° C.) is set to 205 ≦ T ≦ 245 in a specific section has been proposed. Although the principle has not been fully elucidated using this technique, it is described that the occurrence of a draw resonance phenomenon can be suppressed, yarn breakage can be reduced, and further, the fiber uniformity can be improved.

  However, according to the knowledge of the present inventors, the method described in the specification of Patent Document 3 only defines the atmospheric temperature distribution in the yarn traveling direction, and hot air as described in the specification. Even if a circumferential temperature difference occurs in the air flow blown out from the hot air blowing device 3, a tension difference and an accompanying flow difference occur between the yarns in the circumferential direction. The yarn physical properties may be deteriorated by fusing due to yarn swing. Further, according to the knowledge of the present inventors, the atmospheric temperature range described in the specification is as large as 40 ° C. (245−205 = 40 ° C.), and the circumferential air temperature cannot be restricted at all. Similarly to Patent Document 2, circumferential wind temperature spots may occur. Furthermore, according to the knowledge of the present inventors, the amount of heating air in the example described in Patent Document 3 is as extremely small as 1 L / min, and it is clearly insufficient to supply the amount of heating air commensurate with the yarn accompanying flow. This is because the multifilament yarn having a single yarn fineness of 0.28 denier (0.31 dtex), a winding speed of 2000 m / min, and a filament number of 240 has an extremely large woofer spot of less than 1.5%. It is clear from the fact that it is used as a quality judgment criterion for variegation, and it may not be possible to achieve a high thread thickness requirement level such as Wooster variability [H] 0.5% or less. Therefore, the configuration described in the specification of Patent Document 3 with respect to the airflow flowing into the hot air blowing device 3 may not be sufficient to obtain circumferential wind speed uniformity.

  Further, Patent Document 4 discloses a spinning cooling device having an apparatus configuration similar to that of Patent Documents 2 and 3. The configuration of the apparatus disclosed in this document is the same as the configuration shown in FIG. Further, in this document, when winding a yarn at a speed of 5000 m / min or more, an air flow having a temperature of 200 to 500 ° C. is blown from a hot air spraying device 3 having a length of 5 to 20 cm arranged immediately below the spinneret 1. A high-speed spinning method for polyester fibers, in which 0.05 to 0.8 m / second is sprayed onto the yarn 22 and then cold air is blown by the cooling air blowing device 2 arranged immediately below the hot air blowing device 3, has been proposed. When these methods are used, the heated air is supplied from the upper hot air blowing device 3 so that the ascending air flow accompanying the yarn accompanying flow generation and the cooling air supplied from the cooling air blowing device 2 directly flow into the heating region. It is described that it is possible to suppress the variation of the ambient temperature in the heating region. As a result, it is described that it is possible to stably produce polyester fibers and ultrafine multifilaments with excellent uniformity while suppressing yarn breakage and yarn sway.

  However, according to the knowledge of the present inventors, even in the case where the air flow is properly supplied in the yarn traveling direction, as in Patent Document 2 and Patent Document 3, the circumferential direction wind of the air flow blown out from the hot air spraying device 3 If temperature non-uniformity exists, the location where the yarn accompanying flow occurs is different. In other words, the balance of the accompanying flow is lost in a concentric cross section perpendicular to the yarn traveling direction, and contact and fusion between the yarns due to the turbulence of the air flow occurs, and the yarn physical properties are deteriorated. In the apparatus configuration described in the specification of Patent Document 4, it is not specified that a high air temperature air flow is supplied from the outside, and a uniform air temperature is blown in the circumferential direction by the hot air spraying device 3, Feasibility is poor. Therefore, according to the knowledge of the present inventors, if the heat insulating material of the heating cylinder is strengthened, the apparatus main body becomes large, and there are cases where productivity and operability are not preferable in a multi-spindle type spinning facility. Further, as an example of Patent Document 4, a Wuster spot level (0.3 to 0) that can be achieved at a single yarn fineness of 2.08 denier (2.31 dtex), a multifilament with 36 filaments, and a spinning speed of 5500 m / min. .41), for example, may not be applicable to ultrafine multifilaments of 1.0 denier (1.11 dtex) or less.

  Further, Patent Document 5 discloses a spinning cooling device as shown in FIG. In the figure, 24 indicates a blower, and 25 indicates a gas temperature adjuster. In this document, the temperature of the air current, or the temperature and the air volume, is increased stepwise or continuously from the upstream side immediately below the spinneret 1 to the downstream side, and an exhaust fan 24 is provided at one location in the middle part. An exhaust spinning cooling device has been proposed. As a means for this, the cooling zone is divided into two stages and cooling is controlled for each section. As another means, the pitch of the heating wire 26 is arranged in the airflow passage so as to become dense toward the downstream side, As another method, the air flow is heated after being heated by the heat wire 26 and then blown. Alternatively, the air flow passage is formed so as to be gradually narrowed toward the downstream side, or the pressure loss is formed so as to be gradually increased toward the downstream side. There is a method of decreasing the air volume toward the downstream. When these means are used, the spun yarn 22 is weakly cooled on the downstream side, and the yarn physical properties such as elastic modulus and tensile strength are improved by stretching in a state where the temperature difference between the yarn surface and the inside is reduced. However, it is described that yarn breakage can be suppressed, and solidification is promoted by cooling strongly on the upstream side, and contact and fusion between yarns can be suppressed.

  However, according to the knowledge of the present inventors, even if the air flow is properly supplied in the yarn traveling direction, if there is non-uniform circumferential air temperature of the air flow blown out from each cooling zone, it is perpendicular to the yarn traveling direction. In the concentric cross section of the direction, a difference in stretching occurs, and the yarn physical properties may deteriorate.

  In particular, according to the knowledge of the present inventors, in the embodiment of Patent Document 5, the heating wire 26 is circulated in the airflow passage, the pitch of the heating wire 26 is made dense toward the downstream, and the airflow is directly heated. However, because the heating wire 26 is directly placed on the airflow passage to restrict the cross-sectional area of the flow path, and the airflow wind speed is increased or decreased, there is a difference in the amount of heat generated by the airflow from the heating wire 26. , Circumferential wind temperature spots may be exacerbated. Furthermore, since the air flow turbulence and micro vortices are generated due to the non-uniformity of the flow path cross-sectional area, the circumferential wind velocity spots may deteriorate and the circumferential wind temperature spots may deteriorate. Furthermore, providing a heating wire in the airflow passage may make it difficult to seal the airflow passage, and may deteriorate the maintainability of the heating wire 26, which may cause a problem of deterioration in operability.

  In addition, as a result of investigating the uniform wind speed variation in the circumferential direction of the blown air flow of the spinning cooling device, a spinning cooling device as shown in FIG. 16 is shown in Patent Document 6 and FIG. Such a spinning cooling device is disclosed in Patent Document 7. In the figure, 7 is a baffle plate, 5 is a first gas chamber, 6 is a second gas chamber, and 12 is a perforated plate. In the spinning cooling device of Patent Document 6, the baffle plate 7 is configured in the airflow introduction pipe 20 to temporarily collide the airflow against the baffle plate 7 to reduce wind speed spots and to make the wind speed uniform in the circumferential direction. It can be obtained.

Further, in the spinning cooling device of Patent Document 7, two gas chambers, a first gas chamber 5 and a second gas chamber 6, are provided, a perforated plate 12 is provided on the boundary surface, and airflow is supplied to the perforated plate 12. It is described that the air flow turbulence can be reduced and the uniform wind speed in the circumferential direction can be obtained by passing the air through.
However, in each of the above device configurations, the uniform air temperature in the circumferential direction is not clearly stated. According to the knowledge of the present inventors, for example, even if an air flow having a uniform air temperature is supplied from the air flow introduction pipe 20, it is difficult to completely keep the entire spinning cooling device, and heat dissipation cannot be ignored. The air temperature uniformity in the circumferential direction cannot be achieved. In particular, according to the knowledge of the present inventors, in the yarn cooling, it is not the uniform air flow velocity but the uniform air flow rate that determines the main heat transfer coefficient between the yarn and the air flow, which is important for the heat exchange of the yarn. The airflow temperature. In addition, according to the knowledge of the present inventors, for general-purpose polymers such as polyethylene terephthalate and polyamide, by giving a uniform airflow wind speed to the yarn at room temperature air, good thread thickness unevenness and toughness can be obtained. Although it can be obtained, the copolymer polymer has a problem that the toughness is lowered only by giving a uniform air velocity to the room temperature air flow. Therefore, with respect to producing an ultrafine multifilament having a single yarn fineness of 0.1 to 1.6 dtex and a filament number of 2000 or less, yarn contact / fusion due to uneven air temperature in the circumferential direction of the airflow is likely to occur, Such as yarn swaying, thread thickness unevenness and quality such as strength and elongation are extremely deteriorated.Further, fluff and thread breakage occur frequently, and the stability of yarn production deteriorates, and even spinning is not possible. There were many problems.
Japanese Patent Publication No. 38-12364 Japanese Patent Laid-Open No. 55-67007 JP 61-47817 A JP-A-4-41711 Japanese Patent No. 2,674,656 JP 60-126309 A JP-A-48-33113

  The object of the present invention is to provide a yarn having excellent quality such as thickness variation, strength, elongation, etc., excellent in the circumferential air temperature uniformity of the airflow, without contact or fusion of the yarn due to yarn swinging. It is an object of the present invention to provide a spinning cooling device and a melt spinning method that exhibit remarkable effects.

In order to achieve the above object, an spinning cooling apparatus for cooling and solidifying by blowing an air flow inward from the outside of a running path of a yarn obtained by melt spinning a thermoplastic polymer, comprising: an air flow introduction pipe; An airflow passage having an annular flow path that communicates with the airflow introduction pipe and surrounds the outside of the travel path of the yarn, and a heater heat generating portion disposed outside the airflow passage. An outer wall member, a rectifying filter having a flow path that is disposed inside the air flow passage so as to surround the outside of the yarn traveling path, and blows out an air flow inward, and surrounds the outside of the rectifying filter. possess a disposed a cylindrical rectification member, said cylindrical rectifying member is provided spinning annular cooling apparatus characterized by satisfying the following expression.
0.25 ≦ (D _2H −D _2I ) / (D _2O −D _2I ) ≦ 0.75
However, _D2H : Inner diameter (m) of cylindrical rectifying member,
D _2O : the outer diameter (m) of the airflow passage or the second airflow passage,
D _2I : indicates the outer diameter (m) of the rectifying filter.

  Further, according to a preferred embodiment of the present invention, it is located upstream of the air flow passage, surrounds the outside of the yarn travel path, and is disposed so as to cover the entire upstream end of the annular flow passage of the air flow passage. An annular cooling device for spinning having a ring-shaped rectifying member is provided.

  According to a preferred embodiment of the present invention, the air flow passage has a first air flow passage having an annular flow passage disposed so as to surround the outside of the yarn traveling path, and the first air flow passage. A cross-sectional area smaller than the flow path cross-sectional area in a cross section perpendicular to the thread travel path of the first airflow passage, having an annular flow path disposed so as to surround the outside of the travel path of the yarn downstream. There is provided an annular cooling device for spinning composed of a second airflow passage having an area.

  Moreover, according to the preferable form of this invention, the cyclic | annular cooling device for spinning in which the cross-sectional area of the said 1st airflow path and the cross-sectional area of the said 2nd airflow path satisfy | fill the following formula | equation is provided.

0.05 ≦ A _2MIN / A _1MAX ≦ 0.5
Where A _2MIN : the minimum cross-sectional area (m ² ) of the second airflow path,
A _1MAX : Indicates the maximum cross-sectional area (m ² ) of the first airflow passage.

  Further, according to another aspect of the present invention, there is provided an annular cooling device for spinning, which is cooled and solidified by blowing an air flow inward from the outside of a running path of a yarn obtained by melt spinning a thermoplastic polymer, An air flow introduction pipe, a first air flow passage having an annular flow passage communicating with the air flow introduction pipe and surrounding the outside of the traveling path of the yarn, and the downstream of the first air flow passage. An annular flow path disposed so as to surround the outside of the yarn travel path, and having a cross-sectional area smaller than a flow path cross-sectional area in a cross section perpendicular to the thread travel path of the first airflow passage. A second airflow passage, an outer wall member having a heater heat generating portion disposed outside the second airflow passage, the second airflow passage, and the yarn traveling path inside the first airflow passage. Rectification flow with a flow path that is arranged so as to surround the outside and blows airflow inward. Spinning annular cooling device and a motor is provided.

  Further, according to a preferred embodiment of the present invention, it is located upstream of the first air flow passage, surrounds the outside of the yarn travel route, and covers the entire upstream end of the annular flow passage of the first air flow passage. An annular cooling device for spinning having a ring-shaped rectifying member disposed is provided.

  Moreover, according to the preferable form of this invention, the cyclic | annular cooling device for spinning in which the cross-sectional area of the said 1st airflow path and the cross-sectional area of the said 2nd airflow path satisfy | fill the following formula | equation is provided.

0.05 ≦ A _2MIN / A _1MAX ≦ 0.5
Where A _2MIN : the minimum cross-sectional area (m ² ) of the second airflow path,
A _1MAX : Indicates the maximum cross-sectional area (m ² ) of the first airflow passage.

  Moreover, according to the preferable form of this invention, it has a partition plate in the said airflow path along the line radially extended from the virtual center of the said cyclic | annular airflow path, and across the running direction of a thread | yarn. An annular cooling device for spinning is provided.

  According to a preferred embodiment of the present invention, the first air flow path and / or along the line extending radially from the virtual center of the annular first air flow path in the radial direction and over the running direction of the yarn. Alternatively, an annular cooling device for spinning having a partition plate in the second airflow passage is provided.

  Further, according to another aspect of the present invention, when the thermoplastic polymer is melt-spun from the spinneret and airflow is blown inward from the outside of the running path of the spun yarn to cool and solidify, The air flow thus guided is led to an air flow passage having an annular flow passage which is communicated with the air flow introduction pipe and is disposed so as to surround the outside of the traveling path of the yarn, and is then arranged outside the air flow passage. Cylindrical rectification arranged so as to surround the outside of the rectifying filter in each cross section perpendicular to the yarn traveling path of the airflow passage while heating the airflow by an outer wall member having a heater heating portion provided A melt spinning method is provided in which an airflow is guided to a member, and then an airflow is blown inward from an annular rectifying filter disposed inside the airflow passage so as to surround the outside of the traveling path of the yarn.

  Further, according to another aspect of the present invention, when the thermoplastic polymer is melt-spun from the spinneret and airflow is blown inward from the outside of the running path of the spun yarn to cool and solidify, The air flow thus guided is guided to the first air flow passage having an annular flow path which is arranged to communicate with the air flow introduction pipe and surround the outside of the traveling path of the yarn, and then the first air flow From the flow path cross-sectional area in the cross section perpendicular to the thread travel path of the first airflow path, which has an annular flow path disposed so as to surround the outside of the travel path of the yarn downstream of the path The second airflow passage, which is guided to the second airflow passage having a small cross-sectional area, and then heated by an outer wall member having a heater heating portion disposed outside the second airflow passage, 1 Wrap the outside of the yarn travel path inside the airflow path Arranged molten spinning process for blowing out the air flow inwardly from the rectifier filter ring to is provided.

  In the present invention, the “air flow passage” refers to an annular flow passage that is disposed so as to surround the outer side of the yarn traveling path and is sandwiched between an rectifying filter and an outer wall member having a heater heating portion.

  In the present invention, "the outer wall member having a heater heating portion disposed outside the airflow passage" is disposed so as to surround the outer side of the yarn traveling path, and constitutes the outer wall surface of the airflow passage, An outer wall member having a heater heating portion. In this case, the “outer wall member” is preferably an integrally molded member of the heater heating part and the outer wall member, but the heater heating part may be built in the outer wall member, and the heater heating part is disposed on the outer periphery of the outer wall member. May be.

  In the present invention, the “second airflow passage” refers to an annular flow passage which is disposed so as to surround the outside of the yarn traveling path and is sandwiched between the rectifying filter and the outer wall member having the heater heating portion. .

  In the present invention, the “outer wall member having a heater heating portion disposed outside the second airflow passage” is disposed so as to surround the outer side of the yarn traveling path, and the outer wall surface of the second airflow passage. And an outer wall member having a heater heat generating portion. In this case, the “outer wall member” is preferably an integrally molded member of the heater heating part and the outer wall member, but the heater heating part may be built in the outer wall member, and the heater heating part is disposed on the outer periphery of the outer wall member. May be.

  In the present invention, “downstream of the first airflow passage” refers to the downstream of the airflow direction along the first airflow passage.

  In the present invention, the “minimum cross-sectional area of the second airflow passage” refers to the minimum cross-sectional area in a cross section perpendicular to the yarn traveling path of the second airflow passage.

  In the present invention, the “maximum cross-sectional area of the first air flow passage” refers to the maximum cross-sectional area in a cross section perpendicular to the yarn traveling path of the second air flow passage.

  In the present invention, the “inner diameter of the cylindrical rectifying member” refers to an inner diameter in a cross section perpendicular to the travel path of the cylindrical rectifying member.

  In the present invention, the “outer diameter of the airflow passage or the second airflow passage” means an outer diameter in a cross section perpendicular to the traveling path of the yarn in the airflow passage or the second airflow passage.

  In the present invention, the “outer diameter of the rectifying filter” refers to the outer diameter in a cross section perpendicular to the travel path of the rectifying filter. In the present invention, the “yarn traveling route” refers to a main route through which a thermoplastic polymer is melt-spun from an upper spinneret and the spun yarn is wound downward. Here, “upward” means the side close to the spinneret in the traveling direction of the main yarn from which the thermoplastic polymer is melt-spun from the spinneret and the spun yarn is wound, and is wound around the yarn. The side to be taken is called “downward”.

  According to the spinning annular cooling device and the melt spinning method of the present invention, as described above, the circumferential air temperature uniformity of the airflow blown from the spinning annular cooling device is excellent, so that the yarn can be contacted and fused. In addition, a multifilament yarn that is extremely excellent in quality such as unevenness of yarn thickness, strength, and elongation can be obtained with good yarn production and operability.

  Hereinafter, the best embodiment of the cooling device for spinning and the melt spinning method of the present invention will be described in detail with reference to the drawings. FIG. 1 is a schematic longitudinal sectional view of an annular cooling device 100 for spinning used in the first embodiment of the present invention, and FIG. 2 is a view taken along the line AA in FIG. FIG. 6 is a schematic longitudinal sectional view of another preferred embodiment of the spinning annular cooling device 100 used in the first embodiment of the present invention, and FIG. 11 is used in the first embodiment of the present invention. It is a schematic longitudinal cross-sectional view of a melt spinning apparatus.

  As shown in FIG. 11, the melt spinning apparatus used in the first embodiment of the present invention includes a spinneret 1, an annular cooling apparatus 100 for spinning according to the present invention, an oil application apparatus 35, an entanglement application apparatus 40, and a take-up roller 36. , 37 and a winding device 38. In FIG. 11, the yarn 22 spun from the spinneret 1 is cooled by an air current blown from the spinning annular cooling device 100 of the present invention, and after the oil agent is applied by the oil agent applying device 35, the take-up roller 36. , 37 and is wound as a package 39 by the winding device 38. As shown in FIG. 1, an annular cooling device 100 for spinning used in the first embodiment of the present invention includes an air flow introduction pipe 20, an air flow supply port 29 connected from the air flow introduction pipe 20, and the air flow supply opening 29. Are connected so as to surround the outside of the yarn travel path, and are arranged in an annular shape sandwiched between the airflow passage outer wall surface 16 and the inner wall surface 17 and between the airflow passage outer wall surface 16 and the rectifying filter 8. An airflow passage 9 having a flow path, a heater heat generating portion 15 disposed on an outer wall surface 18 constituting the outer periphery of the airflow passage 9, a cylindrical rectifying member 13 that partitions the airflow passage 9 into and out of concentric circles, and a cylinder thereof An annular rectifying filter 8 having a flow path which is disposed inside the straight rectifying member 13 so as to surround the outside of the yarn traveling path and which blows out airflow inwardly. In that case, in the airflow passage 9, a ring-shaped rectifying member 14 is provided which is positioned below the rectifying filter 8 and is disposed so as to cover the entire surface of the annular flow path with respect to a cross section perpendicular to the yarn traveling path. May be.

  Further, as shown in FIG. 4, the heater heat generating portion 15 may cover only the upper part of the outer wall surface 18. Here, FIG. 12 illustrates the relationship between the temperature T (° C.) of the air flow blown from the spinning cooling device used in the first embodiment and the distance L (mm) from the upper end of the rectifying filter 8. is there. In the case of the configuration shown in FIG. 4, as shown by line c in FIG. 12, the air temperature of the airflow blown from the rectifying filter 8 is high only at the upper end of the rectifying filter 8, and the The distribution decreases in temperature. Further, as shown in FIG. 5, the heater heat generating portion 15 may cover only the lower part of the outer wall surface 18. In that case, as shown by line b in FIG. 12, the air temperature of the airflow blown out from the rectifying filter 8 has an air temperature distribution that gently decreases from the upper end of the rectifying filter 8 downward. Also in the second embodiment of the present invention, the airflow temperature can be obtained in the same manner as described above. Therefore, in order to improve the quality such as the strength and elongation of the yarn, an air temperature distribution like the b line having a high slow cooling effect is preferable, and in order to reduce contact and fusion of the yarn 22, c Air temperature distribution like a line is preferable, and the height and arrangement position of the heater heat generating part 15 are arbitrarily set according to the characteristics, desired quality, etc. of the thermoplastic polymer and the multifilament yarn made of thermoplastic polymer. Just do it. Moreover, as shown in FIG. 6, the heater heat generating part 15 may have a multi-stage configuration with two or more stages, and the heat generation capacity of the heater heat generating part 15 may be changed at each stage.

  FIG. 3 is a schematic cross-sectional view of the spinning annular cooling device 100 used in the second embodiment of the present invention, and FIGS. 7 and 8 show the spinning annular cooling device used in the second embodiment. It is a schematic longitudinal cross-sectional view of 100 another preferable form. As shown in FIG. 3, an annular cooling device 100 for spinning used in the second embodiment includes an air flow introduction pipe 20, an air flow supply port 29 connected from the air flow introduction pipe 20, and a lateral direction to the air flow supply opening 29. Are connected to each other and are arranged so as to surround the outside of the yarn traveling path, and are sandwiched between the first airflow passage outer wall surface 30 and the inner wall surface 17, and the first airflow passage outer wall surface 30 and the rectifying filter 8. A first air flow path 10 having a flow path of the first air flow path, an annular flow path positioned downstream of the first air flow path 10 and sandwiched between the second air flow path outer wall surface 31 and the rectifying filter 8, and The airflow passage 10 is disposed on the second airflow passage 11 having a cross-sectional area smaller than the flow passage cross-sectional area in the cross section perpendicular to the yarn traveling path, and the outer wall surface 18 constituting the outer periphery of the second airflow passage 11. Heater heating portion 15, its first air flow passage 10, and second Composed of an annular rectifying filter 8 having a flow passage for blowing out is disposed so as to surround the outer travel path of the yarn inside the flow passage 11 airflow inwardly. In that case, in the first airflow passage 10, a ring-shaped rectifying member 14 that is located below the rectifying filter 8 and is disposed so as to cover the entire surface of the annular flow path with respect to a cross section perpendicular to the yarn traveling path. Further, a cylindrical rectifying member 13 disposed so as to partition a part of the first air flow passage 10 and the second air flow passage 11 into and out of the concentric circles may be formed.

  In addition, as shown in FIG. 7, the heater heat generating portion 15 is disposed on the outer wall surface 18 that forms the outer periphery of the first airflow passage 10, and the outer wall surface 18 that forms the outer periphery of the second airflow passage 11 positioned above the heater heat generating portion 15. Alternatively, the heater heat generating portion 15 may be configured. In that case, preheating of the airflow is performed by the heater heating unit 15 provided with the first airflow passage 10, and main heating is performed by the heater heating unit 15 provided in the second airflow passage 11, thereby 2 It becomes possible to blow out an air flow having a higher air temperature than the step heating. Further, as shown in FIG. 8, a running section 32 is provided between the first airflow passage 10 and the second airflow passage 11, and the flow passage cross-sectional area perpendicular to the yarn traveling route of the first airflow passage 10 is provided. The configuration may be such that it continuously decreases over the run-up section 32 and is connected to the second airflow passage 11. Alternatively, a configuration in which the flow passage cross-sectional area perpendicular to the yarn traveling path of the first airflow passage 10 decreases stepwise over the run-up section 32 and is connected to the second airflow passage 11 may be employed. By providing the run-up section 32, excessive pressure loss can be reduced by suppressing rapid flow path reduction. FIG. 18 is a schematic longitudinal sectional view of another preferred embodiment of the spinning annular cooling device 100 used in the first embodiment of the present invention, and FIG. 19 is a view taken along the line BB in FIG. is there. As shown in FIG. 19, a partition plate 45 is arranged along a line extending radially from the virtual center of the airflow passage 9 in the radial direction and over the running direction of the yarn, and the airflow passage 9 is arranged in the circumferential direction. The structure divided into a plurality of compartments may be used. In that case, the partition plate 45 may be disposed over the entire length of the airflow passage 9 in the traveling direction of the yarn, or may be disposed up to a midpoint of the airflow passage 9. In particular, since the partition plate 45 is disposed over the entire length in the running direction of the yarn, there is no air flow between the compartments partitioned by the partition plate 45, and the air flow can be suppressed in the circumferential direction. The circumferential wind speed uniformity of the airflow blown out from the rectifying filter 8 can be improved. Further, the partition plate 45 is heated from the heater heat generating part 15 through the air flow passage outer wall surface 16 to serve as fins for heating the air flow passing through the air flow passage 9, and as a result, the air flow blown out from the rectifying filter 8. The air temperature can be increased efficiently. Furthermore, heat conduction to the cylindrical rectifying member 13 through the partition plate 45 heats the airflow passing through the cylindrical rectifying member 13, thereby increasing the air temperature of the airflow blown from the rectifying filter 8 more efficiently. be able to. Further, the airflow passage 9 may be divided into four equal parts or 12 equal parts in the circumferential direction by the partition plates 45 arranged radially in the radial direction from the virtual center of the airflow passage 9, and the number of equal parts is not particularly limited. As the number of partition plates 45 increases and the number of equal divisions dividing the airflow passage 9 increases, the surface area of the heating wall surface through which the airflow passes increases, so that the air temperature of the airflow blown from the rectifying filter 8 is efficiently increased. be able to. The partition plate 45 is preferably a flat plate, but may be a porous member. Further, as in the embodiment shown in FIG. 19, the partition plate 45 extends radially in the entire section from the outer peripheral surface of the rectifying filter 8 to the airflow passage outer wall surface 16, thereby forming the outer peripheral surface of the rectifying filter 8. The air flow path 9 to be reached may be completely divided, but the cylindrical flow straightening member 8 may be formed by extending radially in the partial section from the outer peripheral surface of the cylindrical flow straightening member 13 to the air flow passage outer wall surface 16. The air flow channel 9 reaching the outer peripheral surface of the gas may be divided.

  Similarly to the first embodiment of the present invention, the partition plate is provided in the first air flow passage 10 and / or the second air flow passage 11 of the spinning annular cooling device 100 used in the second embodiment of the present invention. 45 may be provided.

  Next, each member common to the first embodiment of the present invention shown in FIG. 1 and the annular cooling device 100 for spinning of the second embodiment of the present invention shown in FIG. Explained.

  Here, the side surface cross-sectional shape (the airflow passage 9 shows the first embodiment of the present invention, the first airflow passage 10 and the second airflow passage 11 show the second embodiment of the present invention), It is not limited to being rectangular, but may be trapezoidal, triangular, pentagonal, polygonal or semicircular, semielliptical, and if the shape in the cross section perpendicular to the running path of the yarn is a double circle, The shape is not particularly limited. However, in this case, the heater heat generating portion 15 is disposed at a position where the flow passage cross-sectional area perpendicular to the yarn traveling path is equal to the upper side so that the air flow is once rectified, and then the heater heat generating portion 15 It is better to heat the airflow at

Next, the heater heat generating portion 15 winds the flexible ribbon heater around the outer wall surface 18 of the airflow passage 9 (first embodiment of the present invention) or the second airflow passage 11 (second embodiment of the present invention). However, it is better to avoid uneven winding. A general-purpose band heater may be attached to the outer wall surface 18, an aluminum cast heater may be attached, a ring heater may be attached, and the type of heater is not particularly limited as long as it has a heat generating part. Absent. Further, the outer wall surface 18 and the heater heat generating part 15 may be an integral mold. Moreover, it is preferable to suppress heat dissipation by attaching a heat insulating material to the outside of the heater heat generating portion 15. What is important here is that the heater heat generating portion 15 is attached to the outer wall surface 18 so that the air flow passage 9 (first embodiment of the present invention) or the second air flow passage 11 (second embodiment of the present invention). ) Through the outer wall surface 18 without disturbing the airflow passing through the airflow). In addition, the heater heat generating portion 15 is preferably installed within an outer diameter range of 90 mm to 300 mm of the outer wall surface 18, and the heater heat generating portion 15 has a height within a range of 10 to 300 mm, more preferably within a range of 50 to 150 mm. It is preferable to install it in Furthermore, the heat generation capacity of the heater heating section 15 is preferably in the range of watt density of 0.5 to 5.0 W / cm ² , more preferably in the range of 1.0 to 3.5 W / cm ^2. . If the watt density is extremely large, such as 5.0 W / cm ² or more, the thermal responsiveness is excellent, but on the other hand, the durability is lowered, so that it is not suitable for long-term use. On the other hand, if the watt density is too small, such as 0.5 W / cm ² , the heater capacity is insufficient, and the air temperature does not rise to an appropriate air blowing temperature.

  Next, the cylindrical rectifying member 13 according to the first and second embodiments of the present invention has a structure that can be easily attached and detached, and is attached to the upper support 33 or the lower support 34 or both. A guide groove is provided and fixed by a bolt or the like, but may be sandwiched between upper and lower supports, or may be fixed to the upper support 33 or the lower support 34 by welding.

  The cylindrical rectifying member 13 is a porous member, and in order to obtain a rectifying effect of the passing airflow, punching metal having a channel opening ratio of 20 to 60% is most suitable, but a laminated structure having a slit channel. A body, a porous ceramic, a wire mesh, or a honeycomb structure. Here, the flow straightening effect of the cylindrical flow straightening member 13 is that the flow path is rapidly reduced and then greatly widened to form a minute turbulent state in a fine space and mixed to uniformize the wind speed difference of the airflow. It becomes possible.

  Further, the length of the cylindrical rectifying member 13 in the running direction of the yarn is preferably equal to the length of the rectifying filter 8 in order to obtain a rectifying effect in the entire length of the rectifying filter 8, or is longer than the total length of the rectifying filter 8. Is set to a length that can include the rectifying filter 8. Further, the cylindrical rectifying member 13 may have two or more multistage configurations having different cylindrical diameters. By setting it as a multistage structure, the airflow rectification effect can be obtained more. Further, as an advantage of the multi-stage configuration, even if the channel opening ratio is set to be somewhat large, the same rectification effect as that of the single-unit cylindrical rectification member 13 can be obtained, so that clogging is suppressed and productivity and operation are reduced. It becomes possible to improve the performance.

  Next, the ring-shaped rectifying member 14 according to the first embodiment and the second embodiment of the present invention has a structure that can be easily attached and detached, and the inner wall surface 17 or the airflow passage outer wall surface 16 or the first. Guide grooves are provided on the outer wall surface 30 of the airflow passage, or both, and are fixed with bolts or the like. The ring-shaped rectifying member 14 is preferably a ring-shaped integrally formed product in consideration of airflow rectifying effects and workability such as attachment / detachment, but it is structurally possible to combine several meniscus shapes into a ring shape. There is no problem. Further, the ring-shaped rectifying member 14 is a porous member, and it is preferable to use a punching metal having a channel opening ratio of 15 to 60%, but it may be a porous ceramic or a wire mesh, It may be a honeycomb structure. In addition, as shown in FIG. 2, as an alternative to the ring-shaped rectifying member 14, the airflow passage 9 having a narrow channel width on the anti-airflow supply port 42 side and a wide channel width on the airflow supply port 29 side is used. By suppressing the increase in the wind speed at the anti-airflow supply port 42, the effect is the same as that of the ring-shaped rectifying member 14 that reduces the pressure imbalance in the circumferential direction. The adjustment of the channel width and the ring-shaped rectifying member 14 may be used in combination. However, equalizing the circumferential pressure by adjusting the flow path width and the corresponding uniform wind speed in the circumferential direction have a large influence of the wind speed distribution on the flow path width, and find the optimum dimensions according to various spinning conditions. In some cases, sufficient consideration is required.

  Next, in the rectifying filter 8 of the first and second embodiments of the present invention, the air flow outlet is opened in the center direction toward the running path of the yarn, and the running direction of the yarn. It is a porous member in which a hole inclined downward from a right angle direction is formed. The airflow is rectified by the rectifying filter 8, and an airflow inclined downward from a direction perpendicular to the yarn traveling direction is formed. The shape of the hole may be a circle, trapezoid, octagon or hexagon, and is an array of holes inclined from the inner diameter to the outer diameter by 5 to 20 degrees over the entire surface. Examples of the porous member in which the inclined holes are formed include a porous member obtained by winding a cellulose ribbon in a spiral shape and thermosetting. This porous member is formed by impregnating a cellulose ribbon (material: paper) with a thermosetting resin (phenolic resin) and then heat-curing to form a gap (pore: about 40 μm) in the ribbon layer. The gaps are uniformly distributed from the outer peripheral side toward the center. And when winding this cellulose ribbon helically, it becomes a structure where a clearance gap inclines toward a center by inclining and winding. Further, instead of the cellulose ribbon, a metal (stainless steel) ribbon may be preliminarily processed with a fine groove and then spirally wound and subjected to high-temperature compression molding. Further, the porous member may be a high-temperature compression-molded metal particle or metal fiber, or a multi-layer structure in which an annular ring having fine slit grooves is formed from the outside toward the center direction, and a high-temperature compression-molded laminated structure. It may be a body. The material of these porous members may be made of paper, wood, or synthetic resin having moderate rigidity, but is preferably made of metal having excellent heat resistance.

  The length of the rectifying filter 8 in the running direction of the yarn includes the maximum thinning deformation position at which the multifilament yarn changes most rapidly, and the length including the cooling and solidifying position of the yarn is the thickness of the yarn. This is a preferred form for plaque suppression. When the air temperature unevenness in the circumferential direction of the air current is bad, a difference occurs in the yarn traveling direction between the maximum thinning deformation position of the yarn and the cooling and solidifying position. In particular, the cooling length, that is, the length of the rectifying filter 8 needs to be lengthened to the extent that a significant difference occurs at the cooling and solidifying position. However, if the circumferential air temperature spot is good, the length of the rectifying filter 8 is reduced. An appropriate length can be obtained. Therefore, the length of the rectifying filter 8 is preferably 50 to 500 mm, and more preferably 100 to 300 mm. Further, the thickness of the rectifying filter 8 is preferably 1 to 20 mm, more preferably 5 to 10 mm, as a thickness that can sufficiently rectify the airflow passing through the slit channel.

  Further, on the contact surface between the rectifying filter 8 and the upper support 33 and the lower support 34, packings 19a and 19b made of silicon and “Teflon (registered trademark)” that maintain airtightness and have excellent heat resistance are attached. It is good. Furthermore, by applying a spring expansion / contraction structure to the lower support 34 and constantly applying a surface pressure to the upper and lower sealing surfaces of the rectifying filter 8, thermal creep deformation of the packings 19a and 19b, air internal pressure fluctuations, or the rectifying filter 8 It can cope with thermal dimensional changes and dimensional changes over time, and can keep airtightness stably and continuously.

  Next, the flow state of the air current in the spinning annular cooling device 100 according to the first embodiment of the present invention will be described with reference to FIGS. FIG. 2 is an AA arrow view of FIG. In the spinning annular cooling device 100 according to the first embodiment of the present invention, the airflow introduction pipe 20 is connected from the lateral direction to the airflow passage 9 having an annular flow channel because of the device configuration for supplying the airflow from the outside. . As shown in FIG. 2, the airflow introduction pipe 20 is radially opened toward the airflow passage 9 to reduce the direct collision of the airflow to the inner wall surface 17 by making the flow passage cross-sectional area slightly larger. It is possible to equalize the airflow passage 9 and reduce circumferential wind speed spots of the airflow blown out from the rectifying filter 8. Therefore, as shown in FIG. 1, the airflow supplied from the outside collides with the baffle plate 7 in the airflow introduction pipe 20, and the airflow VA in which the wind speed spots are once reduced and uniformed is formed. Therefore, first, the air flow VA flows in from the air flow supply port 29 and flows in the circumferential direction through the annular flow path leading to the counter air flow supply side 42, and the air flow that sequentially turns upward and flows toward the ring-shaped rectifying member 14. VU is formed. At that time, the airflow VR flowing in the circumferential direction is changed to the airflow VU, the airflow VU is once formed, and then passed through the ring-shaped rectifying member 14, thereby reducing the circumferential pressure imbalance and the airflow VU. The circumferential wind speed spots can be reduced.

  Next, the airflow VU that has passed through the ring-shaped rectifying member 14 and has improved rectification properties is divided into an airflow VS that flows in the center direction of the filamentous travel path at the same time as forming an airflow VU that flows continuously upward. Is done. The air flow VU and the air flow VS are heated by the heater heat generating portion 15 provided on the outer wall surface 18 and finally blown out from the rectifying filter 8. At that time, the cylindrical rectifying member 13 has a function of changing the direction of the air flow VU to the air flow VS. Therefore, the flow path of the cylindrical rectifying member 13 is rapidly reduced, and then greatly widened, thereby forming a turbulent state in a minute space and mixing it to give a rectifying effect to the air flow VS, thereby causing circumferential wind speed spots. It is possible to reduce the circumferential wind temperature spots.

  Another important function of the cylindrical rectifying member 13 is that the cylindrical rectifying member 13 forms an air flow VU that flows outside the cylindrical rectifying member 13, and the air flow VU that has passed through the ring rectifying member 14 is Directly blowing out from the rectifying filter 8 is reduced, and the airflow VU passing through the space sandwiched between the cylindrical rectifying member 13 and the airflow passage outer wall surface 16 is guided upward. Thereby, by suppressing the decrease in the wind speed of the airflow VU, the heat transfer rate is improved, the amount of heat given to the airflow VU from the heater heat generating part 15 is increased, and the air temperature increase effect of the airflow is obtained. Further, since the airflow blown from the rectifying filter 8 is heated immediately before being blown out, only the minimum necessary airflow can be heated, which is also effective for energy saving. Furthermore, the air flow VU heated by the heater heat generating unit 15 is heated and becomes an upward air flow while being directed upward, and is heated continuously or stepwise by the heater 15. Therefore, the airflow blown out from the rectifying filter 8 can inevitably form a longitudinal air temperature distribution suitable for gradual cooling in which the upper part is a high temperature and the lower part is a low temperature.

  Next, the flow state of the airflow in the spinning annular cooling device 100 of the second embodiment of the present invention will be described with reference to FIG. Here, the flow form from the airflow introduction pipe 20 to the ring-shaped rectifying member 14 is as described above, and the flow form above the ring-shaped rectifying member 14 will be described in detail. The airflow VU that has passed through the ring-shaped rectifying member 14 disposed in the first airflow passage 10 forms an airflow VU that continuously flows upward, and at the same time, is divided into an airflow VS that flows in the center of the yarn travel path and is rectified. Blow out from the filter 8. Furthermore, the airflow VU flowing upward is located downstream of the first airflow passage 10 and has a cross-sectional area smaller than the flow passage cross-sectional area in the cross section perpendicular to the yarn travel path of the first airflow passage 10. The air is guided to the passage 11, heated by the heater heat generating portion 15 disposed outside the second air flow passage 11, and blown out from the rectifying filter 8.

Here, the flow cross-sectional area of the second airflow passage 11 connected to the first airflow passage 10 is reduced, thereby restricting the airflow VU going upward through the second airflow passage 11, and the rectification filter of the second airflow passage 11. The air flow blown out from the air flow 8 is reduced, and the air flow blown out from the rectifying filter 8 in the first air flow passage 10 is increased. Thereby, the airflow volume heated by the heater heating part 15 can be reduced, the thermal efficiency can be increased, and the air temperature can be improved. Furthermore, as an important effect of reducing the flow passage cross-sectional area of the second airflow passage 11, since the heater heat generating portion 15 can be reduced in diameter, heat radiation from the heater heat generating portion 15 can be reduced, and the influence of disturbance can be reduced. The temperature of the second airflow passage 11 can be equalized. Furthermore, it can cope with energy saving. Moreover, since it can heat immediately before blowing out from the rectification filter 8, it is hard to receive the influence of a disturbance, Therefore It becomes possible to blow out the airflow of appropriate wind temperature. The reduction rate of the cross-sectional area of the flow path is _expressed by the following equation (the maximum flow-path cross-sectional area A _1MAX (m ² ) of the first airflow passage 10 and the minimum flow-path cross-sectional area A _2MIN (m ² ) of the second airflow passage 11. By setting it as the range of 1), the circumferential wind velocity spot of the airflow VU can be reduced, and the circumferential wind temperature uniformization from the rectification filter 8 can be achieved.

0.05 ≦ A _2MIN / A _1MAX ≦ 0.5 (1)
Here, in the case of A _2MIN / A _1MAX ≦ 0.05, the flow restriction in the second air flow passage 11 becomes excessive, so that circumferential wind speed spots of the air flow VU occur, and the heater heat generating portion 15 A difference occurs in the amount of heat applied to the airflow VU from the airflow, and circumferential air temperature spots of the airflow blown out from the rectifying filter 8 are generated. In the case of 0.5 ≦ A _2MIN / A _1MAX , the air velocity of the air flow in the second air flow passage 11 is too low, and the heat transfer rate is small when the air flow VU passes through the heater heat generating portion 15, so that heat is transmitted. Cannot be heated sufficiently. Further, by providing the cylindrical rectifying member 13 in the first air flow passage 10 and the second air flow passage 11, the air flow VS has a rectifying effect as described above, and circumferential wind speed spots of the air flow blown out from the rectifying filter 8 are reduced. It is possible to reduce the circumferential wind temperature spots.

Next, in order to achieve uniform circumferential air temperature variation in the airflow blown from the rectifying filter 8, a space disposed inside the cylindrical rectifying member 13 and sandwiched between the rectifying filters 8, and the cylindrical rectifying member 13, the space sandwiched between the airflow passage outer wall surface 16 (the first embodiment of the present invention) or the space sandwiched between the second airflow passage outer wall surface 31 (the second embodiment of the present invention) and The volume ratio is important. Therefore, the inner diameter D _2H (m) of the cylindrical rectifying member 13, the outer diameter D _{2O of} the airflow passage 9 (first embodiment of the present invention), or the second airflow passage 11 (second embodiment of the present invention). ( _M ) By setting the outer diameter D _2I (m) of the rectifying filter 8 within the range of the following equation (2), the circumferential wind speed and the circumferential air temperature of the airflow blown from the rectifying filter 8 are made uniform. it can.

0.25 ≦ (D _2H −D _2I ) / (D _{2 O−} D _2I ) ≦ 0.75 (2)
Therefore, in the case of (D _2H −D _2I ) / (D _2O −D _2I ) ≦ 0.25, the gap between the rectifying filter 8 and the cylindrical rectifying member 13 is minimized, so that the air flow VS is cylindrical. After passing through the rectifying member 13, widening is possible, and after passing through the cylindrical rectifying member 13, it flows into the rectifying filter 8 as a jet, so that circumferential wind speed spots are deteriorated. In the case of 0.75 ≦ (D _2H −D _2I ) / (D _2O −D _2I ), the cylindrical rectifying member 13 and the airflow passage outer wall surface 16 (the first embodiment of the present invention) or the first 2 The flow path of the outer wall 31 of the airflow passage (second embodiment of the present invention) is narrowed, so that circumferential wind speed spots of the airflow VU flowing on the outer peripheral side of the cylindrical rectifying member 13 are generated and the heater generates heat. A difference is generated in the amount of heat applied to the airflow VU from the section 15, and circumferential wind temperature spots of the airflow blown out from the rectifying filter 8 are generated.

  Therefore, in the annular cooling device 100 for spinning of the present invention, the circumferential air temperature spot in the airflow blown out from the rectifying filter 8 is 50% or less (± 25% or less) at each height of the rectifying filter 8, particularly Since it is important for slow cooling of the yarn, 30% or less can be achieved in the range of 50 mm downward from the upper end of the rectifying filter 8.

  Further, the annular cooling device of the present invention is not limited to the single spindle type described above, but can be applied to a multi-cylinder type annular cooling device as shown in FIG. In that case, a cylindrical airflow passage outer wall surface 16 is formed on the outer periphery of the rectifying filters 8 arranged at regular intervals so as to allow airflow to flow from below, thereby forming an airflow passage 9. A cylindrical rectifying member 13 for partitioning into and out of the concentric circle is provided, and a heater heating unit 15 is provided on the outer wall surface 18 of the airflow passage 9 to heat the airflow.

  Next, the yarn cooling effected by the flow form of the airflow blown inward from the rectifying filter 8 according to the first and second embodiments of the present invention will be described with reference to FIG. FIG. 14 is a schematic view showing the flow form of the airflow blown out from the spinning annular cooling device 100 of the present invention. When the multifilament yarn 22 having a single yarn fineness of 0.1 to 1.6 dtex or less and a filament number of 2000 or less is spun, a yarn accompanying flow VZ is generated along with the thinning and solidification of the yarn, and in the running direction of the yarn. Since a large amount of airflow flows, a vacuum state in which the air is insufficient is formed in the vicinity immediately below the spinneret 1, and ascending airflow VV is generated at the center of the spinneret 1 in order to compensate for the insufficient air. Therefore, in the annular cooling device 100 for spinning of the present invention, the air blow start distance (hereinafter referred to as the cooling start distance QTD) from the spinneret 1 surface to the upper end of the rectifying filter 8 is shortened, and further, the yarn associated flow VZ is reduced. By supplying an appropriate air flow from the rectifying filter 8, a multifilament yarn 22 having good yarn spots can be obtained. Furthermore, by supplying a heated air flow from the rectifying filter 8, the thinning and solidification behavior of the yarn 22 can be delayed, that is, it can be gradually cooled. The slow cooling mentioned here means that high elongation can be achieved by reducing the deformation speed of the yarn 22, and high stress can be achieved by suppressing stress concentration in the thinning behavior. In addition, the strength and elongation can be improved by gradual cooling, and then the cooling and strengthening can be avoided thereafter to avoid contact and fusion of the yarn 22.

  Furthermore, since the circumferential wind velocity spots and circumferential wind temperature spots of the airflow blown out from the rectifying filter 8 are small, and an appropriate air volume can be provided for cooling and solidifying the yarn 22 as described above, the circle of the rising airflow VZ Since circumferential wind velocity spots are reduced, surface temperature spots on the spinneret 1 are eliminated, and fineness spots can be reduced. Further, since the surface temperature unevenness of the spinneret 1 is eliminated, the cooling start distance QTD can be further shortened, so that the yarn-making property when the multifilament yarn 22 is manufactured is stabilized, and a yarn having good yarn physical property unevenness is obtained. It is done. What is important here is that the flow form of the airflow immediately below the spinneret 1 is greatly different from that of giving a high-temperature atmosphere just below the spinneret 1 and blowing out the high-temperature airflow as in the annular cooling device 100 for spinning of the present invention. It is. An accompanying flow VZ is generated immediately below the spinneret 1 due to the thinning and solidification behavior of the spun yarn 22. This is because, even under a high temperature atmosphere, the generation of the yarn accompanying flow VZ is somewhat reduced due to the delay of the thinning behavior, but the pressure immediately below the base is reduced by the generated yarn accompanying flow VZ, so that the rising air flow VV is higher than the supply / exhaust balance. Always occurs. Since this updraft VV is a low-temperature cooling air, it generates atmospheric temperature spots. On the other hand, the annular cooling device 100 for spinning of the present invention continuously blows out the high-temperature air flow from the rectifying filter 8 immediately below the spinneret 1, so that the air deficient in the yarn accompanying flow VZ can be compensated. Further, by blowing out the high temperature air flow, the atmosphere temperature just below the spinneret 1 can be improved, and the spinneret 1 surface can be indirectly heated to stabilize the spinnability.

  The present invention is an extremely versatile invention and is suitable for all multifilament yarns obtained by a spinning cooling device and a melt spinning method. Therefore, it is not particularly limited by the thermoplastic polymer constituting the multifilament yarn. For example, polyesters, polyamides, polyphenylene sulfides, polyolefins, polyethylenes, polypropylenes, etc. can be cited as examples of thermoplastic polymers constituting the multifilament yarns suitable for the present invention.

  An example of a polyester suitable for the present invention is a thermoplastic polymer synthesized from, for example, a dicarboxylic acid or an ester-forming derivative thereof and a diol or an ester-forming derivative thereof, and used as a molded article such as a fiber, a film, or a bottle. Can be mentioned. Specific examples of polyesters include, for example, polyethylene terephthalate, polytrimethylene terephthalate, polybutylene terephthalate, polylactic acid, polyethylene naphthalate, polybutylene naphthalate, polypropylene terephthalate, polytetramethylene terephthalate, polyethylene-2, 6- Naphthalenedicarboxylate, polyethylene-1,2-bis (2-chlorophenoxy) ethane-4,4'-dicarboxylate, and the like. In the above, polyethylene terephthalate is the most versatile, but the present invention is also suitable for polyethylene terephthalate or polyester copolymers mainly containing ethylene terephthalate units. In addition, various ester-forming derivatives may be copolymerized within a range that does not impair the spinning stability. For example, in a polyester cation dyeable yarn capable of being dyed with excellent sharpness, an ester-forming derivative having a sodium sulfonate group is generally 10 mol% or less as long as the yarn-making stability is not impaired. Although copolymerized, such a thing may be sufficient.

  Examples of polyamides suitable for the present invention include nylon 6, nylon 66, and the like. The present invention is also suitable for nylon 6 and nylon 66.

  The present invention is also suitable for a cellulose ester-based thermoplastic polymer containing a plasticizer. Cellulose ester refers to those in which the hydroxyl group of cellulose is blocked by an ester bond, and specific examples include esters with carboxylic acids such as cellulose acetate, cellulose acetate propionate, cellulose acetate butyrate, and cellulose acetate phthalate. It may have a bond, may have an ester bond with oxylcarboxylic acid such as lactic acid, glycolic acid, hydroxy acid or a polymer thereof, caprolactone, propiolactone, valerolactone, pivalolactone, etc. It may be a cyclic ester or an ester thereof with a polymer thereof, or a mixed ester thereof. These celluloses may contain a plasticizer. Specific examples of the plasticizer include, for example, those having a relatively low molecular weight such as dimethyl phthalate, diethyl phthalate, dihexyl phthalate, dioctyl phthalate, dimethoxyethyl phthalate, ethyl Phthalic acid esters such as phthalyl ethyl glucoat, butyl phthalyl butyl glycate, aromatic polyvalent carboxylic acid esters such as tetraoctyl pyromellitate, trioctyl trimellitate, dibutyl adipate, dioctyl adipate, dibutyl sebacate , Aliphatic polycarboxylic acid esters such as dioctyl sebacate, diethyl azate, dibutyl azate, dioctyl azate, etc., lower polyhydric alcohols such as glycerin triacetate and diglycerin tetraacetate Fatty acid esters include triethyl phosphate, tributyl phosphate, tributoxyethyl phosphate, phosphoric acid esters such as tricresyl phosphate and the like. Specific examples of the plasticizer include, for example, aliphatic polyesters composed of glycol and dibasic acid such as polyethylene adipate, polybutylene adipate, polyethylene succinate, polybutylene succinate, and the like having a relatively high molecular weight. And aliphatic polyesters composed of oxycarboxylic acids such as polylactic acid and polyglycolic acid, aliphatic polyesters composed of lactones such as polycaprolactone, polypropiolactone and polyvalerolactone, and vinyl polymers such as polyvinylpyrrolidone. These plasticizers can be used alone or in combination.

  Furthermore, in the above-mentioned thermoplastic polymer, within a range not impairing the yarn production stability, matting agent such as titanium dioxide, silicon oxide, kaolin, anti-coloring agent, stabilizer, antioxidant, deodorant, flame retardant, Various functional particles such as yarn friction reducing agents, color pigments, surface modifiers, and additives such as organic compounds may be contained, and copolymerization may be included.

  In addition, the thermoplastic polymer used in the present invention may be composed of a single component or a plurality of components. In the case of a plurality of components, examples of the configuration include a core sheath and a side-by-side configuration. In addition, the cross-sectional shape of the multifilament yarn may be an irregular shape such as a circle, a triangle, a flat shape, or a hollow shape.

The present invention is an extremely versatile invention and is suitable for all multifilament yarns obtained by a spinning cooling device and a melt spinning method. Therefore, it is not particularly limited by the single yarn fineness of the multifilament yarn. For example, the single yarn fineness before drawing or when wound without being drawn, or the single yarn fineness after drawing or drawing / false twisting may be in the range of 0.1 to 10 dtex. Further, the single yarn fineness after drawing or drawing / false twisting may be in the range of 0.1 to 3.2 dtex or 0.2 to 3.2 dtex. Furthermore, the single yarn fineness after drawing or drawing / false twist is 0.1 to 3.1 dtex, or 0.1 to 3.0 dtex, or 0.1 to 2.9 dtex, or 0.1 to 2 .8 dtex, alternatively 0.1-2.7 dtex, alternatively 0.1-2.6 dtex, alternatively 0.1-2.5 dtex, alternatively 0.1-2.4 dtex, alternatively 0.1-2 .3 dtex, or 0.1-2.2 dtex, alternatively 0.1-2.1 dtex, alternatively 0.1-2.0 dtex, alternatively 0.1-1.9 dtex, or 0.1-1 It may be in the range of .8 dtex, or 0.1 to 1.7 dtex, or 0.1 to 1.6 dtex. The smaller the single yarn fineness, the clearer the difference from the prior art.
The present invention is an extremely versatile invention and is suitable for all multifilament yarns obtained by a spinning cooling device and a melt spinning method. Therefore, it is not particularly limited by the number of single filaments of the multifilament yarn. For example, the number of single filaments of the multifilament yarn may be in the range of 30 to 2000 or 50 to 2000. The number of single filaments of the multifilament yarn may be in the range of 30 to 1900. Further, the number of single filaments of the multifilament yarn is 30 to 1800, alternatively 30 to 1700, alternatively 30 to 1600, alternatively 30 to 1500, alternatively 30 to 1400, alternatively 30 to 1300, alternatively 30 to 1200. Or 30 to 1100, alternatively 30 to 1000, alternatively 30 to 900, alternatively 30 to 800, alternatively 30 to 700, alternatively 30 to 600. The greater the number of single filaments of the multifilament yarn, the clearer the difference from the prior art.

Each characteristic value used in the examples was determined by the following measurement method.
(1) Thread thickness spots, Wooster spots [H]:
Using a USTER TESTER UT-4 manufactured by ZELLWEGER USTER, Wooster spots [H] measured with a thread speed of 100 m / min, a supply tension of 1/30 g / dtex, a twister rotation speed of 8000 rpm for 5 minutes, and evaluated by HInert were “0”. .. less than .4 ”,“ 0.4 or more and less than 0.6 ”as“ ◯ ”, and“ 0.6 or more and less than 1.0 ”as x.
(2) Strength / Elongation / Strong Elongation Product, Toughness Using a TENSILON RTC-1210A manufactured by ORIENTEC, a test length of 200 mm arbitrarily cut from the manufactured yarn (multifilament yarn) was pulled at a pulling speed of 200 mm / min. The measured strength / elongation was evaluated as toughness with “less than 20” as x, “20 or more but less than 30” as ◯, and “30 or more” as ◎ with respect to the product of strong elongation obtained from the following formula.

Strong elongation product = strength (cN / dtex) × (elongation (%)) ^1/2
(3) Airflow blowout wind speed:
The airflow blowing air velocity is measured at room temperature and normal humidity using an anemometer master anemometer (Nippon Kanomax Co., Ltd .: MODEL6004) or Cambridge Accusens anemometer (Degree Controls Inc .: UAS1100PC). This is the one measured by installing in a gap of 5 mm to 10 mm from the inner peripheral surface of the rectifying filter 8 toward the center.
(4) Circumferential wind velocity unevenness, circumferential wind velocity non-uniformity:
Circumferential wind velocity spots are the airflow blown air velocity at the rectifying filter 8 in a room of normal temperature and humidity, with the airflow supply port 29 being 0 degrees in the circumferential direction, 8 points in 45 degree increments, the yarn traveling direction 3 points, 8 points x 3 points = 24 points from the upper end of the rectifying filter 8 as 10 mm position, 30 mm position, 50 mm position (the following [1] to [3] formulas), and the circumference at each height position The average value of the directional wind speed values of 8 points is calculated (the following [4] equation), the variation rate with the measured value is obtained at each height position (the following [5] equation), and the total variation rate (ΔV _10i , ΔV _30i). , ΔV _50i : i = 0 to 315, 45 degrees).
[1] Wind speed at 10 mm position from the upper end of the rectifying filter 8; V _10i (i = 0 to 315, 45 degrees)
[2] Wind speed at 30 mm position from the upper end of the rectifying filter 8; V _30i (i = 0 to 315, 45 degrees)
[3] Wind speed at 50 mm position from the upper end of the rectifying filter 8; V _50i (i = 0 to 315, 45 degrees)
[4] Average wind speed at positions 10, 30, and 50 mm from the upper end of the rectifying filter 8:
V _10ave = (Sum (V _10i )) / 8
V _30ave = (Sum (V _30i )) / 8
V _50ave = (Sum (V _50i )) / 8 (i = 0 to 315, 45 degrees)
[5] The wind speed fluctuation rate from the wind speed average value at positions 10, 30, and 50 mm from the upper end of the rectifying filter 8;
ΔV _10i = (V _10i −V _10ave ) / V _10ave
ΔV _30i = (V _30j −V _30ave ) / V _30ave
ΔV _50i = (V _50j −V _50ave ) / V _50ave (i = 0 to 315, 45 degrees)
(5) Spinnability:
Execute spinning for 36 hours with 36 spindles, and evaluate the number of breaks during this period. ◎ "less than 1" is ◎, "1 to less than 2" is ◯, "2 to less than 3" Δ, “3 times or more” was evaluated as x.
(6) Airflow supply air volume:
The airflow supply airflow rate Q (m ³ / sec) to the spinning cooling device is set at the inlet of the airflow supply port 29 of the spinning cooling device in a room at normal temperature and humidity, and the differential pressure before and after the orifice is calculated. Measured and calculated as air volume.
(7) The longitudinal wind speed distribution of the air flow blown from the rectifying filter 8 is the wind speed of the air flow blown from the outer periphery of the rectifying filter 8 toward the center, and the air flow supply port 29 is set to 0 degree in the circumferential direction. 8 points every 45 degrees, 0 mm, 10 mm, 30 mm, 50 mm, 100 mm, 150 mm, 200 mm, 250 mm, 300 mm from the upper end of the rectifying filter 8 in the yarn traveling direction (height direction of the rectifying filter 8) Measured at 8 points, 8 points x 8 points = 64 points at 0 mm, 0 mm, 10 mm, 30 mm, 50 mm position, 50 mm and later at 50 mm intervals), and each rectifier filter 8 height What calculated the average value.
(8) Airflow blowout air temperature:
The airflow temperature of the airflow is such that a K-type thermocouple or a temperature measurement sensor probe is installed in the gap of 5 mm to 10 mm from the inner peripheral surface of the rectifying filter 8 toward the center, and the air temperature fluctuation rate is within 1 ° C./min. Say what you measure when you become.
(9) Circumferential wind temperature spots:
As the blowout air temperature from the rectifying filter 8, the air flow supply port 29 is set to 0 degree in the circumferential direction, 8 points in 45 degree increments, and 0 mm, 10 mm, 30 mm, 50 mm, 100 mm from the upper end of the rectifying filter 8 in the yarn running direction. Maximum air temperature at each height of 150 mm, 200 mm, 250 mm, 300 mm (when the total length of the rectifying filter 8 is 300 mm or more, 0 to 50 mm is measured at 0 mm, 10 mm, 30 mm, 50 mm positions, and 50 mm and later at 50 mm intervals) Tmax, the minimum air temperature Tmin, and the average air temperature Tave are obtained and calculated from the following formula.
Circumferential wind temperature spot (%) = (maximum wind temperature Tmax−minimum wind temperature Tmin) / average wind temperature Tave × 100
(10) Intrinsic viscosity [η]
Measurement was performed at 25 ° C. using orthochlorophenol as a solvent.
[Example 1]
Copolymerization of dimethyl isophthalate containing a metal sulfonate group with 3.0 wt% and 1.0 wt% of PEG with respect to the dicarboxylic acid component has an intrinsic viscosity [η] of 0.70, and titanium oxide as a matting agent is 0.00. Polyethylene terephthalate containing 30 wt% is spun from the spinneret 1 at a single hole discharge rate of 0.15 g / min, cooled by using the spinning annular cooling device 100 of the second embodiment of the present invention, and the oil agent applying device 35. After applying the oil agent, the multifilament yarn was manufactured by winding at a speed of 2175 m / min. At that time, the distance from the lower surface of the spinneret 1 to the upper end of the rectifying filter 8 (cooling start distance QTD) was set to 26.5 mm. As shown in FIG. 3, the spinning annular cooling device 100 includes a first air flow passage 10 and a second air flow passage 11, and the opening ratio 40.3% (hole diameter 2 mm, pitch 3 mm) in the first air flow passage 10. Punching metal having a staggered arrangement and a plate thickness of 1.5 mm was arranged as the ring-shaped rectifying member 14. The outer diameter of the first airflow passage 10 is 170 mm, the inner diameter is 110 mm (matches the outer diameter of the rectifying filter 8), the outer diameter of the second airflow passage 11 is 137 mm (matches the outer wall surface 31 of the second airflow passage), and the inner diameter is 110 mm (rectifying filter). 8) and the second airflow passage 11 on the downstream side of the ring-shaped rectifying member 14 and the second airflow passage 11, the aperture ratio is 40.3% (hole diameter 2mm, pitch 3mm, staggered arrangement, plate thickness). A cylindrical rectifying member 13 (inner diameter 126 mm / outer diameter 129 mm) in which a 1.5 mm) punching metal was formed in a tube shape was disposed. The rectifying filter 8 is a porous member (inner diameter of 97 mm, outer diameter of 110 mm, height of 300 mm) in which a metal ribbon (material: SUS304) with fine grooves is spirally wound and compression-molded at a high temperature. Was inclined 15 degrees downward from a right angle direction). Further, the heater heat generating portion 15 has a two-stage configuration with an inner wall surface 140 (outer diameter 140 mm) of the second airflow passage 11 having an inner diameter of 140 mm and a rectifying filter 8 at the upper end and a height of 70 mm and 100 mm. A band heater having a watt density of 3.0 W / cm ² was provided, and the surface temperature of the band heater heating part was controlled by a temperature control panel so as to be 300 ° C.

Using the spinning cooling device 100 for spinning, 33 dtex, 144 filament yarns and 2 yarns of polyester ultrafine fibers were produced. At this time, as a result of supplying an air flow of 49.9 m ³ / hour and normal temperature of 20 ° C. from the air flow introduction pipe 20, the air temperature of the air flow blown from the upper end of the rectifying filter 8 is 180 ° C., and the circumferential air temperature spot is 8 It was 5%. At that time, air was used as the airflow. As shown in Table 1, the best results were obtained for spinning, and the Worcester spots of the obtained ultrafine fibers were the best, and the toughness was good.

[Example 2]
Example 2 will be described as an example in which the polyethylene terephthalate equivalent to Example 1 was spun with the same fineness, and the spinning annular cooling device 100 of the first embodiment of the present invention was used. In addition, Example 2 is a reference example. As shown in FIG. 1, the spinning cooling device 100 for spinning includes an airflow passage 9, an outer diameter of the airflow passage 9 is 137 mm (matches the outer wall surface 16 of the airflow passage), and an inner diameter is 110 mm (matches the outer diameter of the rectifying filter 8). ). The ring-shaped rectifying member 14 has a punching metal having an aperture ratio of 40.3% (hole diameter 2 mm, pitch 3 mm, staggered arrangement, plate thickness 1.5 mm) disposed in the airflow passage 9, and the cylindrical rectifying member 13 has an opening. A punching metal having a rate of 40.3% (hole diameter 2 mm, pitch 3 mm, staggered arrangement, plate thickness 1.5 mm) in a tube shape (inner diameter 126 mm / outer diameter 129 mm) was disposed in the airflow passage 9. Further, the rectifying filter 8 has the same dimensions and the same specifications as those of the first embodiment, and the heater heat generating part 15 has a band heater having the same specifications as that of the first embodiment and has a height of 70 mm from the upper end of the rectifying filter 8 downward. It was arranged in a two-stage configuration of 100 mm, and was controlled by a temperature control panel so that the surface temperature of the band heater heating part was 300 ° C.

Using the above spinning cooling apparatus 100 for spinning, 33 dtex, 144 filament yarns, and two filaments of ultrafine fibers were produced. At this time, as a result of supplying an air flow of 49.9 m ³ / hour and normal temperature of 20 ° C. from the air flow introduction pipe 20, the air temperature of the air flow blown from the upper end of the rectifying filter 8 is 180 ° C., and the circumferential air temperature spot is 8 It was 2%. As shown in Table 1, the best results were obtained for spinning, and the Worcester spots of the obtained ultrafine fibers were the best, and the toughness was good.
[Example 3, Example 4, Example 5]
Next, Example 3, Example 4, and Example 5 are demonstrated as an Example with the same structure of the cyclic | annular cooling apparatus 100 for spinning as Example 2, and equivalent polyethylene terephthalate and a single yarn fineness differing. In addition, these Example 3, Example 4, and Example 5 are reference examples. In Example 3, 56 dtex, 144 filament yarns, 1 filament ultrafine fiber in Example 4, 66 dtex, 144 filament yarns, 1 filament ultrafine fiber in Example 5, 84 dtex, 144 filament yarns, 1 yarn extra fine fiber were produced. At that time, the single-hole discharge rate discharged from the spinneret 1 was 0.39 g / min in Example 3, 0.46 g / min in Example 4, and 0.59 g / min in Example 5. As shown in Table 1, in Example 3 where the single yarn fineness was the smallest, Wooster spots were good results, and in Examples 4 and 5 other than that, the best results were obtained for yarn production, fiber Wooster spots and toughness. Obtained.
[Example 6]
Example 6 will be described as an example of another preferred embodiment of the spinning annular cooling device 100 according to the second embodiment of the present invention, which is spun with polyethylene terephthalate equivalent to Example 1. The ratio of the flow path cross-sectional area in the cross section perpendicular to the yarn running direction of the first air flow passage 10 to the cross section of the flow path cross section in the cross section perpendicular to the yarn running direction of the second air flow path 11, and the cylindrical rectifying member 13 The influence on the circumferential wind spot was confirmed. As described in the first embodiment, the spinning annular cooling device 100 used in the sixth embodiment has the same configuration except that the cylindrical rectifying member 13 is removed. The first airflow passage 10 has an outer diameter of 177 mm and an inner diameter of 110 mm (matches the outer diameter of the rectifying filter 8), and the second airflow passage 11 has an outer diameter of 116 mm (matches with the second airflow passage outer wall surface 31) and an inner diameter of 110 mm (rectification) The outer diameter of the filter 8). Further, as the heater heating section 15, the outer wall surface 18 (outer diameter 119 mm) of the second airflow passage 11 has a three-stage configuration with an inner diameter of 119 mm and a height of 50 mm × 3 pieces = 150 mm with the rectifying filter 8 facing downward at the upper end. Each stage was provided with a band heater with a watt density of 3.0 W / cm ² , and the surface temperature of the band heater heating part was controlled with a temperature control panel so as to be 300 ° C.

Using the spinning cooling device 100 for spinning, 56 dtex, 96 filament yarns, and two filaments of ultrafine fibers were produced. At that time, the single hole discharge amount discharged from the spinneret 1 was 0.48 g / min. At this time, as a result of supplying an air flow of 43.7 m ³ / hour and normal temperature of 20 ° C. from the air flow introduction pipe 20, the air temperature of the air flow blown from the upper end of the rectifying filter 8 is 200 ° C., and the circumferential air temperature spot is 15 It was 9%. In Example 6, since there is no cylindrical rectification member 13 and a rectification effect cannot be obtained, the circumferential wind temperature spots tend to be slightly worsened, and the flow width of the second airflow passage 11 is reduced. The heat receiving efficiency from the heater heat generating part 15 was improved, and the air temperature of the airflow blown out from the upper end of the rectifying filter 8 tended to be high. As shown in Table 1, the best results were obtained for spinning, and the Worcester spots of the obtained ultrafine fibers were the best, and the toughness was good.
[Example 7]
Next, Example 7 explains the yarn unevenness and the toughness effect when the lower limit of the parameter range of the following expression is exceeded.

0.05 ≦ A _2MIN / A _1MAX ≦ 0.5
_{However, A 2MIN:} minimum cross-sectional area of the second air flow passage ^(m _{2), A 1MAX:} indicates the maximum cross-sectional area of the first air flow passage ^{(m 2).}

The spinning annular cooling device 100 used in Example 7 has an outer diameter of 114.3 mm (matching with the second airflow passage outer wall surface 31) and an inner diameter of 110 mm (matching with the outer diameter of the rectifying filter 8). The cylindrical rectifying member 13 was removed. The rest of the configuration was the same as in Example 1, and the temperature was controlled by a temperature control panel so that the surface temperature of the band heater heating part was 300 ° C. At this time, as a result of supplying an air flow of 43.7 m ³ / hour and normal temperature of 20 ° C. from the air flow introduction pipe 20, the air temperature of the air flow blown from the upper end of the rectifying filter 8 is 210 ° C., and the circumferential air temperature spot is 16 It was 3%. In Example 7, since there is no cylindrical rectifying member 13 and the rectifying effect cannot be obtained, the circumferential wind temperature spots tend to be slightly worsened, and the flow width of the second airflow passage 11 is further reduced. As a result, the heat receiving efficiency from the heater heat generating portion 15 is improved, and the air temperature of the airflow blown out from the upper end of the rectifying filter 8 is increased. As shown in Table 2, compared to Example 1, Wooster spots [H] showed a tendency to deteriorate, but the product of strong elongation was improved and the spinning performance during spinning was good. Good results were obtained with Worcester spots and toughness of the fine fibers.

[Example 8, Example 9]
Next, the upper limit area of the parameter range of the following expression, the yarn unevenness when the upper limit is exceeded, and the effect of toughness will be described in Embodiments 8 and 9.

0.05 ≦ A _2MIN / A _1MAX ≦ 0.5
_{However, A 2MIN:} minimum cross-sectional area of the second air flow passage ^(m _{2), A 1MAX:} indicates the maximum cross-sectional area of the first air flow passage ^{(m 2).}

The spinning annular cooling device 100 used in Example 8 has an outer diameter 144 mm (matching with the second airflow passage outer wall surface 31), an inner diameter 110 mm (matching with the outer diameter of the rectifying filter 8) of the second airflow passage 11, and others. Is the same apparatus configuration as that of the first embodiment, and in the ninth embodiment, the outer diameter of the second airflow passage 11 is 154 mm (matches the outer wall surface 31 of the second airflow passage), and the inner diameter is 110 mm (matches the outer diameter of the rectifying filter 8). Other than that, the apparatus configuration was the same as in Example 1. In both Examples 8 and 9, the surface temperature of the band heater heating portion was controlled by the temperature control panel so as to be 300 ° C. At this time, as a result of supplying an airflow of 43.7 m ³ / hour and normal temperature of 20 ° C. from the airflow introduction pipe 20, the air temperature of the airflow blown out from the upper end of the rectifying filter 8 is 180 ° C. in the circumferential direction in Example 8. The wind spot was 8.4%, and in Example 9, the wind spot was 170 ° C. and the circumferential wind spot was 8.9%. As shown in Table 2, the ratio of the channel cross-sectional area in the cross section perpendicular to the yarn running direction of the first airflow passage 10 and the flow path cross-sectional area in the cross section perpendicular to the yarn running direction of the second airflow passage 11 is The larger the value, the lower the air temperature of the airflow blown from the upper end of the rectifying filter 8, so that the product of high elongation decreases. However, the spinning performance during spinning is good, and the obtained Worcester spots of the ultrafine fiber, Toughness gave good results.
[Actual施例10, Example 11]
Next, the yarn unevenness in the parameter limit range of the following formula, in the toughness change real施例10 will be described yarn plaques parameter limit range, the toughness effects in Example 11.

0.25 ≦ (D _2H −D _2I ) / (D _2O −D _2I ) ≦ 0.75
However, _D2H : The inside diameter (m) of a cylindrical rectification member, _D2O : The outer diameter (m) of an airflow path or a 2nd airflow path, _D2I : The outer diameter (m) of a rectification filter is shown.

At that time, the cylindrical rectifying member 13, the aperture ratio 40.3% (pore size 2 mm, pitch 3 mm, the staggered arrangement, the thickness 1.5 mm) punched metal is obtained by the tubular, the actual施例10, place in inside diameter 119 mm (outer diameter 122 mm), in example 11, was placed at the inner diameter 129 mm (outer diameter 132 mm), another device configuration of its was made to be the same as in example 1. Further, actual施例10, Example 11, the co, as the surface temperature of the band heater heat generating portion becomes 300 ° C., it was controlled at a temperature control panel. At this time, the supply air volume 43.7m ³ / time from the airflow inlet pipe 20, as a result of supplying the normal temperature 20 ° C. in a stream of air temperature of the air blown out from the upper end of the rectifying filter 8, the actual施例10 180 ° C., the circumferential direction wind Yutakamadara stood 14.4%, 200 ° C. in example 11, the circumferential wind Yutakamadara was Tsu Do 15.9%. As described in Table 2, the gap between the inner diameter of the cylindrical rectifying member 13 and the flow path sandwiched between the outer peripheral surfaces of the rectifying filter 8, and the second airflow passage outer wall surface 31 and the outer peripheral surface of the rectifying filter 8 The larger the ratio with the gap distance of the flow path, the narrower the width of the flow path between the outer peripheral surface of the cylindrical rectifying member 13 and the outer wall surface 31 of the second airflow passage, and the heat receiving efficiency from the heater heat generating part 15 is improved. Thus, the wind temperature of the air flow blown out from the upper end of the rectifying filter 8 rose, and as a result, the result of increasing the strength elongation product was obtained . Also, Example 10, in Example 11, spinnability upon spinning the best results, and Worcester plaques obtained ultrafine fibers, toughness and good results were obtained.
[Example 12 ]
Next, Example 12 describes the yarn unevenness and the toughness effect when the partition plate 45 is disposed in the spinning annular cooling device 100 of the second embodiment. In addition to the same annular cooling device 100 for spinning as in the tenth embodiment, the partition plates 45 are radially arranged in the first airflow passage 10 and the second airflow passage 11 so as to be 12 evenly in the running direction of the yarn. The temperature was controlled by a temperature control panel so that the surface temperature of the band heater heating part was 300 ° C. At this time, as a result of supplying an air flow of 43.7 m ³ / hour and normal temperature of 20 ° C. from the air flow introduction pipe 20, the air temperature of the air flow blown from the upper end of the rectifying filter 8 is 190 ° C., and the circumferential wind temperature spot is It was 12.3%. The partition plate 45 serves as a heating fin, and the air temperature of the airflow rises. Further, by dividing the annular channel in the circumferential direction, the airflow in the circumferential direction is restricted, and the wind speed and air temperature in the circumferential direction are limited. Since the spots were suppressed, the best results were obtained for the spinning performance during spinning, and the wooster spots and toughness of the obtained ultrafine fibers were satisfactory.
[Comparative Example 1]
In the structure of the spinning annular cooling device 100 used in Example 1, the spinning annular cooling device in which the cylindrical rectifying member 13 and the heater heating portion 15 were removed was used in Comparative Example 1. In other respects, polyethylene terephthalate equivalent to Example 1 and ultrafine fibers were obtained under the same spinning conditions. At this time, as a result of supplying the air flow of 49.9 m ³ / hour and normal temperature of 20 ° C. from the air flow introduction pipe 20, the air temperature of the air flow blown from the upper end of the rectifying filter 8 is 25 ° C., and the circumferential air temperature spot is 16 It was 5%. As a result, as shown in Table 1, the spinning performance during spinning was good and the Worcester spots of the obtained ultrafine fibers were good, but the toughness deteriorated.
[Comparative Example 2]
Next, in the structure of the annular cooling device 100 for spinning used in Comparative Example 1, the cylindrical rectifying member 13 is removed, and the flow path cross-sectional area A _{1MAX in the} cross section perpendicular to the yarn traveling direction of the first airflow passage 10 is An annular cooling device for spinning in which the ratio of the flow passage cross-sectional area _{2MIN in} the cross section perpendicular to the yarn running direction of the second airflow passage 11 was 0.04 was used in Comparative Example 2. In other respects, polyethylene terephthalate equivalent to Example 1 and ultrafine fibers were obtained under the same spinning conditions. At this time, as a result of supplying the air flow of 49.9 m ³ / hour and normal temperature of 20 ° C. from the air flow introduction pipe 20, the air temperature of the air flow blown from the upper end of the rectifying filter 8 is 210 ° C., and the circumferential air temperature spot is 21 It worsened to 3%. As a result, as shown in Table 1, the spinning performance during spinning was good and the toughness of the obtained ultrafine fibers was good, but the Wooster spots were deteriorated.
[Comparative Example 3]
Polyethylene terephthalate equivalent to Example 4 and equivalent fibers (66 dtex, 144 filament yarns, one yarn) were obtained using a cross flow type spinning cooling device. As shown in Table 1, the yarn breakage stopped several times during spinning, and the yarn-making property was poor, and the Worcester spots of the obtained fiber were poor.
[Comparative Example 4]
In the same manner as in Comparative Example 3, a polyethylene terephthalate equivalent to Example 5 and equivalent fibers (84 dtex, 144 filament yarns, one yarn) were obtained using a cross-flow type cooling device for spinning. As shown in Table 1, the Worcester spots of the obtained fibers were relatively good, but the yarn breakage stopped several times during spinning, and the yarn-making property deteriorated.
[Comparative Example 5]
In the structure of the spinning annular cooling device 100 used in Example 1, the cylindrical rectifying member 13 is made of a punching metal having an aperture ratio of 40.3% (hole diameter 2 mm, pitch 3 mm, staggered arrangement, plate thickness 1.5 mm). It was in a tube shape and was arranged with an inner diameter of 113 mm (outer diameter of 116 mm), and the other device configuration was the same as in Example 1. Further, similarly to Examples 10 and 11, the temperature was controlled by the temperature control panel so that the surface temperature of the band heater heating portion was 300 ° C. At this time, as a result of supplying an air flow of 43.7 m ³ / hour and normal temperature of 20 ° C. from the air flow introduction pipe 20, the air temperature of the air flow blown from the upper end of the rectifying filter 8 is 170 ° C., and the circumferential air temperature spot is It became 23.2%. As a result, as shown in Table 2, when the gap ratio is small, the air current cannot be widened after passing through the cylindrical rectifying member 13, the circumferential wind speed and wind spot are deteriorated, and the Worcester spot of the obtained ultrafine fiber is obtained. Got a tendency to get worse.
[Comparative Example 6]
In the structure of the annular cooling device 100 for spinning used in Comparative Example 5, the cylindrical rectifying member 13 is made of a punching metal having an aperture ratio of 40.3% (hole diameter 2 mm, pitch 3 mm, staggered arrangement, plate thickness 1.5 mm). It was in a tube shape and was arranged with an inner diameter of 132 mm (outer diameter of 135 mm), and the other device configuration was the same as in Example 1. Further, similarly to Comparative Example 5, the temperature of the band heater heating part was controlled by the temperature control panel so that the surface temperature would be 300 ° C. At this time, as a result of supplying an air flow of 43.7 m ³ / hour and normal temperature of 20 ° C. from the air flow introduction pipe 20, the air temperature of the air flow blown from the upper end of the rectifying filter 8 is 210 ° C., and the circumferential wind temperature spot is It became 20.7%. As a result, as shown in Table 2, when the gap ratio is increased, the flow path width between the outer peripheral surface of the cylindrical rectifying member 13 and the second airflow passage outer wall surface 31 is narrowed. In addition, the circumferential wind temperature spots deteriorated, and the Worcester spots of the obtained ultrafine fibers were deteriorated.

  The present invention is not limited to a spinning cooling device for spinning ultrafine multifilament yarn for clothing, but can also be applied to a spinning cooling device for industrial nylon yarn, a spinning cooling device for industrial tetron yarn, and the like. The application range is not limited to these.

1 is a schematic cross-sectional view of a spinning cooling device used in a first embodiment of the present invention. It is an AA arrow line view of FIG. It is a schematic sectional drawing of the cooling device for spinning used for the 2nd Embodiment of this invention. It is a schematic sectional drawing of the other preferable form of the cooling device for spinning used for the 1st Embodiment of this invention. It is a schematic sectional drawing of the other preferable form of the cooling device for spinning used for the 1st Embodiment of this invention. It is a schematic sectional drawing of the other preferable form of the cooling device for spinning used for the 1st Embodiment of this invention. It is a schematic sectional drawing of the other preferable form of the cooling device for spinning used for the 2nd Embodiment of this invention. It is a schematic sectional drawing of the other preferable form of the cooling device for spinning used for the 2nd Embodiment of this invention. It is a schematic sectional drawing of the cooling device for spinning of a prior art example. It is a schematic sectional drawing of the cooling device for spinning of a prior art example. It is a schematic longitudinal cross-sectional view of the melt spinning apparatus used for the 1st Embodiment of this invention. The relationship between the temperature T (° C.) of the air flow blown from the spinning cooling device used in the first embodiment or the second embodiment of the present invention and the distance L (mm) from the upper end of the rectifying filter is illustrated. Is. 1 is a schematic cross-sectional view of a multi-spindle spinning cooling device used in a first embodiment of the present invention. It is the schematic diagram which showed the flow form of the airflow which blown off from the cyclic | annular cooling device for spinning used for the 1st Embodiment or 2nd Embodiment of this invention. It is a schematic sectional drawing of the cooling device for spinning of a prior art example. It is a schematic sectional drawing of the cooling device for spinning of a prior art example. It is a schematic sectional drawing of the cooling device for spinning of a prior art example. It is a schematic sectional drawing of the other preferable form of the cooling device for spinning used for the 1st Embodiment of this invention. It is a BB arrow line view of FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Spinneret 2 Cooling air spraying device 3 Hot air spraying device 4 Focusing guide 5 1st gas chamber 6 2nd gas chamber 7 Baffle plate 8 Rectification filter 9 Airflow path 10 1st airflow path 11 2nd airflow path 12 Perforated plate 13 Cylindrical rectifying member 14 Ring-shaped rectifying member 15 Heater heating portion 16 Outer wall surface of airflow path 17 Inner wall surface 18 Outer wall surface 19a 19b Packing 20 Airflow introduction pipe 22 Yarn (multifilament yarn)
DESCRIPTION OF SYMBOLS 23 Spinning hole 24 Blower 25 Gas temperature regulator 26 Heating wire 27 Spin pack 28 Spin block 29 Airflow supply port 30 1st airflow path outer wall surface 31 2nd airflow path outer wall surface 32 Run-up section 33 Upper support body 34 Lower support body 35 Oil agent Giving device 36 37 Take-up roller 38 Winding device 39 Package 40 Entangling device 42 Anti-air flow supply port 43 Cooling tube 44 Heating tube 45 Partition plate 100 Annular cooling device for spinning VA In the air flow supply port, wind speed spots are reduced and uniformized. Airflow VR Flowing air flowing from the air supply port to the anti-airflow supply port along the outer wall surface VU Airflow passage, or the airflow flowing upward through the first airflow passage and the second airflow passage VS Concentric in the direction perpendicular to the yarn traveling direction Airflow flowing in the center direction VZ Yarn accompanying flow VV Upflow air QTD Cooling start distance

Claims (5)

An annular cooling device for spinning, in which an airflow is blown inward from the outside of a running path of a yarn obtained by melt spinning a thermoplastic polymer, and solidified by cooling.
An air flow introduction pipe,
A first airflow passage having an annular flow path that is in communication with the airflow introduction pipe and is disposed so as to surround the outside of the travel path of the yarn ;
A flow in a cross section perpendicular to the yarn traveling path of the first airflow passage, having an annular flow path disposed so as to surround the outside of the yarn traveling path downstream of the first airflow passage. A second airflow passage having a cross-sectional area smaller than the road cross-sectional area ;
An outer wall member having a heater heat generating portion disposed outside the second airflow passage, or outside the first airflow passage and the second airflow passage ;
A rectifying filter having a flow path that is disposed inside the first air flow path and the second air flow path so as to surround the outside of the traveling path of the yarn and blows out the air flow inward;
Wherein and a disposed a cylindrical rectification member so as to surround the outer rectification filter, said cylindrical rectifying members, following spinning annular cooling device, characterized by satisfying the expressions.
0.25 ≦ (D _2H −D _2I ) / (D _2O −D _2I ) ≦ 0.75
However, _D2H : Inner diameter (m) of cylindrical rectifying member,
D _2O : outer diameter (m) of the second airflow path,
D _2I : indicates the outer diameter (m) of the rectifying filter. A ring-shaped rectifying member that is located upstream of the first airflow passage , surrounds the outside of the travel path of the yarn, and is disposed so as to cover the entire upstream end of the annular flow path of the first airflow passage ; The annular cooling device for spinning according to claim 1, characterized in that: The annular cooling device for spinning according to claim 1 or 2 , wherein a cross-sectional area of the first airflow passage and a cross-sectional area of the second airflow passage satisfy the following expression.
0.05 ≦ A _2MIN / A _1MAX ≦ 0.5
Where A _2MIN : the minimum cross-sectional area (m ² ) of the second airflow path,
A _1MAX : Indicates the maximum cross-sectional area (m ² ) of the first airflow passage. A partition plate is provided in the first airflow passage and / or the second airflow passage along a line extending radially from the virtual center of the annular first airflow passage and in the running direction of the yarn. The annular cooling device for spinning according to claim 1 or 2, characterized by comprising: When the thermoplastic polymer is melt-spun from the spinneret and air is blown inward from the outside of the running path of the spun yarn to cool and solidify,
The air flow guided from the air flow introduction pipe is led to the first air flow path having an annular flow path which is arranged to communicate with the air flow introduction pipe and surround the outside of the travel path of the yarn ,
Thereafter, a cross-section perpendicular to the yarn travel path of the first airflow path has an annular flow path disposed so as to surround the outside of the travel path of the yarn downstream of the first airflow path. Leading to a second airflow passage having a smaller cross-sectional area than
After that, while heating the airflow with an outer wall member having a heater heat generating portion arranged outside the second airflow passage or outside the first airflow passage and the second airflow passage , guide the air flow in a cylindrical rectifying members satisfying the disposed the following equation so as to surround the outside of rectifier filter in each cross section perpendicular to the travel path, the rectifier filter first airflow passage and the second air flow It is annularly arranged inside the passage so as to surround the outside of the traveling path of the yarn,
Then, melt spinning method characterized by blowing the air flow inwardly from the rectifying filter.
0.25 ≦ (D _2H −D _2I ) / (D _2O −D _2I ) ≦ 0.75
However, _D2H : Inner diameter (m) of cylindrical rectifying member,
D _2O : outer diameter (m) of the second airflow path,
D _2I : indicates the outer diameter (m) of the rectifying filter.

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