EP3121312A1

EP3121312A1 - Yarn cooler

Info

Publication number: EP3121312A1
Application number: EP16179202.3A
Authority: EP
Inventors: Jun Sawada; Kinzo Hashimoto; Jun Kikuchi; Kazuhiro Kawamoto; Jumpei Suzuki
Original assignee: TMT Machinery Inc
Current assignee: TMT Machinery Inc
Priority date: 2015-07-22
Filing date: 2016-07-13
Publication date: 2017-01-25
Anticipated expiration: 2036-07-13
Also published as: EP3121312B1; JP2017025434A; JP6522452B2; CN106367821B; CN106367821A

Description

BACKGROUND OF THE INVENTION

The present invention relates to a yarn cooler configured to cool yarns spun out downward from a spinneret.
There have been known yarn coolers each configured to cool yarns spun out from a spinneret, such as a yarn cooler disclosed in Patent Literature 1 (Japanese Unexamined Patent Publication No. 2008-231607 ) . In this yarn cooler, a buffer chamber in which cooling air flows upward is formed around a cylindrical member structuring a peripheral wall of a yarn running space, and yarns are cooled by the cooling air entering from the buffer chamber to the yarn running space. Now, if there is a time variation in the flow of the cooling air entering into the yarn running space, unevenness in terms of cooling may be caused in the yarns, leading to deterioration in quality of the yarns. In this regard, it is important to restrain the time variation in the flow of the cooling air. To deal with this, Patent Literature 1 discloses that one or more porous plates (flow adjustment members) are provided in the buffer chamber. Particularly in FIG. 3 (2), there is disclosed a multiple-stage configuration in which a plurality of porous plates are provided.

SUMMARY OF THE INVENTION

However, Patent Literature 1 totally fails to disclose how the porous plates are designed in terms of their properties in such a multiple-plate configuration where the plurality of porous plates are provided. Further, the above literature merely describes the advantageous effect brought about by the multiple-plate configuration as follows: even though the porosity of the porous plates is somewhat increased, the effect of flow adjustment is substantially equivalent to that in a single-plate configuration where a single porous plate is provided; and thus clogging in the porous plates is prevented. That is to say, the technique of the Patent Literature 1 is not intended to actively improve the effect of flow adjustment by the multiple-plate configuration, as compared to that in the single-plate configuration.
An object of the present invention is to actively improve the effect of flow adjustment in a yarn cooler including a plurality of porous plates, as compared with the configuration of a single porous plate, and to effectively restrain a time variation in the flow of cooling air entering into a yarn running space.
To achieve the above obj ect, the present invention provides a yarn cooler configured to cool a yarn spun out downward from a spinneret, the yarn cooler including: a cooling cylinder provided below the spinneret to be opposed to the spinneret, the cooling cylinder including therein a yarn running space through which the yarn is runnable, an upper peripheral wall of the yarn running space forming a flow adjustment section configured to adjust the flow of cooling air entering into the yarn running space while a lower peripheral wall of the yarn running space forming a impassable section configured to prevent the cooling air from entering into the yarn running space; an accommodation box accommodating the cooling cylinder, to which box the cooling air is supplied through a supply portion provided at a lower portion of the accommodation box; a first porous plate disposed in a supply passage where the cooling air supplied through the supply portion flows upward along the impassable section, the first porous plate being configured to adjust the flow of the cooling air; and a second porous plate disposed above and apart from the first porous plate in the supply passage, the second porous plate being configured to further adjust the flow of the cooling air having been adjusted by the first porous plate, wherein the thickness ratio of the second porous plate is smaller than the thickness ratio of the first porous plate.
In this arrangement, the flow of the cooling air supplied through the supply portion of the accommodation box is first adjusted by the first porous plate and then adjusted by the second porous plate, and thereafter, the flow of the cooling air enters into the yarn running space through the flow adjustment section of the cooling cylinder. By designing the porous plates so that the thickness ratio of the second porous plate is smaller than the thickness ratio of the first porous plate, the directions of the flow of the cooling air and the flow rates of the cooling air are uniformized, and thereby the time variation in the flow of the cooling air entering into the yarn running space is effectively restrained. This will be detailed later.
Further, in the present invention, it is preferable that the thickness ratio of the first porous plate is not less than 0.7 and not more than 1.6, and it is more preferable that the thickness ratio of the first porous plate is not less than 0.8 and not more than 1.2.
As will be described later, by designing the thickness ratio of the first porous plate as above, the directions of the flow of the cooling air having passed through the first porous plate are paralleled to an upward direction more successfully, and this further promotes the uniformity in the directions of the flow and the flow rates of the cooling air having passed through the second porous plate finally.
In addition, it is preferable that the average porosity of the second porous plate is equal to or larger than the average porosity of the first porous plate.
If the pressure loss (fluid resistance) in the second porous plate is larger than the pressure loss in the first porous plate, it is difficult for the cooling air having passed through the first porous plate to smoothly pass through the second porous plate, which may hinder the flow of the cooling air. For this reason, the average porosity of the second porous plate is designed to be equal to or larger than the average porosity of the first porous plate. This limits the pressure loss in the second porous plate to a predetermined value or less, to ensure the smooth flow of the cooling air.
Furthermore, it is preferable that the distance between the first porous plate and the second porous plate is not less than 20 mm and not more than 80 mm.
If the distance between the first porous plate and the second porous plate is too large, the flow of the cooling air, the directions of which have been adjusted by the first porous plate to be parallel to the upward direction, may be disturbed before reaching the second porous plate. Meanwhile, if the distance between the first porous plate and the second porous plate is too small, the flow of the cooling air passing through the first porous plate is likely to be affected by the second porous plate, and this may cause unsuccessful flow adjustment by the first porous plate. Thus, by defining the distance between the first porous plate and the second porous plate as being not less than 20 mm and not more than 80 mm, the effect of the flow adjustment brought about by the use of the first porous plate and the second porous plate is reliably improved.
Furthermore, it is preferable that a plurality of the cooling cylinders are accommodated in the accommodation box.
In this arrangement, when sets of yarns are respectively spun out from a plurality of spinnerets, the sets of the yarns are simultaneously cooled in the respective cooling cylinders. When the plurality of cooling cylinders are disposed in the accommodation box, the variation in the flow of the cooling air among the different cooling cylinders tends to be larger because the spaces around the cooling cylinders are different in shape from one another. In this regard, with the present invention, such a variation is able to be decreased well.
In the present invention, by designing the thickness ratio of the second porous plate to be smaller than the thickness ratio of the first porous plate, the effect of flow adjustment is actively improved as compared with the configuration of the single porous plate, and the time variation in the flow of the cooling air entering into the yarn running space is effectively restrained.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a partial cross section of a melt spinning device including a yarn cooler of the present invention.
FIG. 2 is a cross section taken along II-II in FIG. 1.
FIG. 3 is a schematic diagram of an analytical model.
FIG. 4 is a vector diagram showing the flow of the cooling air obtained through analysis.
FIG. 5 is a schematic diagram of an analytical model.
FIG. 6 is a vector diagram showing the flow of cooling air obtained through analysis.
FIG. 7 is a cross section schematically showing the flow of the cooling air.

DESCRIPTION OF THE PREFERRED EMBODIMENTS

The following will describe an embodiment of a yarn cooler of the present invention.

[Melt spinning device]

FIG. 1 is a partial cross section of a melt spinning device including the yarn cooler of the present invention. FIG. 2 is a cross section taken along II-II in FIG. 1. As shown in FIG. 1, a melt spinning device 1 includes a spinning beam 2, a yarn cooler 3, oiling devices 4, and the like. The spinning beam 2 is provided with a plurality of pack housings 11. In each pack housing 11, a spinning pack 12 is disposed. The spinning pack 12 stores therein molten material to be formed into yarns Y, such as molten polyester. A spinneret 13 is provided at a lower end portion of each spinning pack 12. The molten material stored in the spinning pack 12 is spun out downward as the yarns Y from a plurality of through holes (not illustrated) formed in the spinneret 13. It should be noted that the spinnerets 13 are arranged in a staggered arrangement in two rows each extending in a left-right direction, in the same manner as cooling cylinders 31 which will be described later (see FIG. 2).
The yarn cooler 3 is disposed below the spinning beam 2. The yarn cooler 3 is configured to cool the yarns Y, which are spun out downward from the spinnerets 13 in the spinning beam 2, by cooling air supplied through a duct 5. The oiling devices 4 are disposed below the yarn cooler 3. The oiling devices 4 are configured to apply oil to the yarns Y cooled by the yarn cooler 3. The yarns Y to which oil has been applied by the oiling devices 4 are wound onto bobbins by an unillustrated winding device which is disposed below the oiling devices 4.

[Yarn cooler]

The yarn cooler 3 is configured to cool the yarns Y by the cooling air supplied through the duct 5. The yarn cooler 3 includes a substantially rectangular-parallelepiped accommodation box 30 which accommodates the plurality of cooling cylinders 31. The accommodation box 30 is provided with a supply portion 30a at its lower back end portion. The supply portion 30a is connected with the duct 5, and the cooling air supplied through the duct 5 flows into the accommodation box 30 via the supply portion 30a.
As shown in FIG. 2, the cooling cylinders 31 are arranged in a staggered arrangement in two rows each extending in the left-right direction. The staggered arrangement of the cooling cylinders 31 (and the spinnerets 13) enables the cooling cylinders 31 to be arranged densely, to improve the production efficiency of the yarns Y. The supply portion 30a is provided to cover the entire length of the accommodation box 30 in the left-right direction, which is a lined-up direction in which the cooling cylinders 31 are lined up in each row. This structure enables the cooling air to be supplied substantially uniformly to the cooling cylinders 31 lined up in the lined up direction.
Description continues referring back to FIG. 1. Each cooling cylinder 31 has a substantially cylindrical shape, and is disposed below the corresponding spinneret 13 so as to be opposed to the spinneret 13. Each cooling cylinder 31 penetrates the accommodation box 30 in an up-down direction. The inside of each cooling cylinder 31 is a yarn running space 32 extending in the up-down direction. The yarns Y spun out from the spinneret 13 run downward in the yarn running space 32. A peripheral wall of the yarn running space 32, i.e., a cylinder body of the cooling cylinder 31 is structured so that its upper portion forms a flow adjustment section 33, while its lower portion forms an impassable section 34.
The flow adjustment section 33 is structured to include a first flow adjustment member 33a and a second flow adjustment member 33b provided inside the flow adjustment member 33a. The first flow adjustment member 33a is formed by perforated metal, for example. The first flow adjustment member 33a is configured to adjust the flow so that the flow of the cooling air enters into the yarn running space 32 substantially horizontally. The second flow adjustment member 33b is formed by multi-layer metal wire mesh, for example. The second flow adjustment member 33b is configured to uniformize the flow of the cooling air entering into the yarn running space 32. The impassable section 34 is made of material through which the cooling air is impassable, so that the cooling air does not enter into the yarn running space 32 through the impassable section 34.
The cooling air entering through the supply portion 30a to the accommodation box 30 flows along the cooling cylinders 31, through a portion of the space in the accommodation box 30 in which portion no cooling cylinder 31 is disposed (this portion is hereinafter referred to as a "supply passage 35"). Finally, the cooling air passes through the flow adjustment section 33 of each cooling cylinder 31 and then enters into the yarn running space 32 (see arrows in FIG. 7) . If the cooling air enters into the yarn running space 32 without sufficient flow adjustment, there may be caused a time variation in the flow of the cooling air, possibly leading to unevenness in the yarns Y in terms of cooling. In view of the above, in the yarn cooler 3, a first porous plate 36 and a second porous plate 37 are provided at a portion of the supply passage 35 which is around the impassable sections 34 , i.e., at the portion where the cooling air flows upward along the impassable sections 34. With this arrangement, the flow adjustment of the cooling air is effectively performed.
It should be noted that the supply passage 35 is actually a single space as shown in FIG. 2. In the cross section of FIG. 1, the supply passage 35 is illustrated as if it is divided. For the sake of convenience, the reference sign is given to each of the divided parts of the supply passage in FIG. 1, though the supply passage is a single space. The same applies to FIG. 3, FIG. 5, and FIG. 7.
The first porous plate 36 is disposed substantially horizontally to be substantially level with an upper end of the supply portion 30a. The first porous plate 36 is formed by perforated metal, for example. The second porous plate 37 is disposed, not less than 20 mm and not more than 80 mm above the first porous plate 36. The second porous plate 37 is disposed substantially horizontally to be substantially level with upper ends of the impassable sections 34. Similarly to the first porous plate 36, the second porous plate 37 is also formed by perforated metal, for example. In the present embodiment, the first and second porous plates 36 and 37 are designed so that the thickness ratio of the second porous plate 37 is smaller than the thickness ratio of the first porous plate 36. This will be detailed later.

[Study on porous plates]

The present inventors conducted fluid analysis for wholehearted consideration on how the effect of flow adjustment can be improved in the configuration of multiple porous plates. FIG. 3 is a schematic diagram of an analytical model. The detailed dimensions are indicated in FIG. 3. Analysis was conducted for 6 cases shown in Table 1 under the condition that: the cooling air enters from the supply portion 30a at a flow rate of 0.437 m³/min; and an upper end of the supply passage 35 is open to the atmosphere. Table 1 shows the dispersion in the in-plane velocity of the cooling air having passed through the last porous plate (i.e. , the second porous plate 37 in each of Cases A to E, or the first porous plate 36 in Case F) . Further, FIG. 4 is a vector diagram showing the flow of the cooling air obtained through the analysis. Note that "porosity" used herein means an average porosity on the entire surface of the porous plate, i.e., the ratio of the total sum of the areas of all the holes to the entire area of the porous plate (the holes may be arranged regularly or irregularly). Further, "thickness ratio" used herein means the ratio of the thickness of the plate to the diameter of the hole.

[Table 1]

	Case A		Case B		Case C
	First porous plate	Second porous plate	First porous plate	Second porous plate	First porous plate	Second porous plate
Plate thickness t [mm]	1.6	0.8	1.6	1.6	0.8	1.6
Hole diameter d [mm]	2	2	2	2	2	2
Thickness ratio t/d [-]	0.8	0.4	0.8	0.8	0.4	0.8
Porosity [%]	29.6	49.7	29.6	29.6	49.7	29.6
Dispersion in in-plane velocity (standard deviation) at 1 mm above the last porous plate	1.91284		3.04940		3.08742
Dispersion in in-plane velocity (standard deviation) at 5 mm above the last porous plate	0.59582		0.97709		1.10766
Dispersion in in-plane velocity (standard deviation) at 10 mm above the last porous plate	0.48911		0.80593		0.91697

	Case D		Case E		Case F
	First porous plate	Second porous plate	First porous plate	Second porous plate	First porous plate	Second porous plate
Plate thickness t [mm]	0.8	0.4	1.6	0.8	1.6	-
Hole diameter d [mm]	2	2	2	2	2	-
Thickness ratio t/d [-]	0.4	0.2	0.8	0.4	0.8	-
Porosity [%]	29.6	49.7	49.7	49.7	29.6	-
Dispersion in in-plane velocity (standard deviation) at 1 mm above the last porous plate	2.04426		1.88220		3.31466
Dispersion in in-plane velocity (standard deviation) at 5 mm above the last porous plate	0.76864		0.61748		1.23981
Variation in in-plane velocity (standard deviation) at 10 mm above the last porous plate	0.66238		0.60356		1.03116

The dispersion in velocity is improved in each of Cases A to E where both the first porous plate 36 and the second porous plate 37 are provided, as compared to Case F where the single porous plate is provided. This shows that the effect of the flow adjustment is improved by providing the plurality of porous plates. However, in Cases B and C, the dispersion in velocity is just a little improved as compared with Case F, and in addition, there were observed relatively larger swirls in the flow of the cooling air having passed through the second porous plate 37, as can be clearly seen in FIG. 4. Meanwhile, in Cases A, D, and E, the dispersion in velocity is significantly improved as compared to Case F. Further, no noticeable swirl was found in the flow of the cooling air having passed through the second porous plate 37 in FIG. 4.
Among Cases A, D, and E, in which the improvement is larger, there is a common condition: the thickness ratio of the second porous plate 37 is smaller than the thickness ratio of the first porous plate 36. Meanwhile, in Cases B and C in which the improvement is smaller, the thickness ratio of the second porous plate 37 is equal to or larger than the thickness ratio of the first porous plate 36. Based on the above finding, the present inventors arrives at the consideration that: when the thickness ratio of the second porous plate 37 is designed to be smaller than the thickness ratio of the first porous plate 36, the directions of the flow of the cooling air are first paralleled to the upward direction to some extent by the first porous plate 36, and then the flow rates of the cooling air is uniformized by the second porous plate 37, and thereby the effect of the flow adjustment is actively improved.

The present inventors further examined an optimum range of the thickness ratio of the first porous plate 36 through fluid analysis, in order to improve the effect of paralleling the directions of the flow of the cooling air to the upward direction by the first porous plate 36. FIG. 5 is a schematic diagram of an analytical model. The detailed dimensions are indicated in FIG. 5. Analysis was conducted for 5 cases shown in Table 2 under the condition that: the cooling air enters from the supply portion 30a at a flow rate of 0.437 m³/min; and the upper end of the supply passage 35 is open to the atmosphere. Note that how well the directions of the flow of the cooling air are paralleled to the upward direction by the first porous plate 36 is influenced mainly by the thickness ratio, and little by the porosity.

[Table 2]

	Case 1	Case 2	Case 3	Case 4	Case 5
Plate thickness t [mm]	0.8	1.4	1.6	2.3	3.2
Hole diameter d [mm]	2	2	2	2	2
Thickness ratio t/d [-]	0.4	0.7	0.8	1.15	1.6
Porosity [%]	29.6	29.6	29.6	29.6	29.6

FIG. 6 is a vector diagram showing the flow of the cooling air obtained through the analysis. In Case 1 (the thickness ratio is 0.4), the flow of the cooling air, which has flowed from the right to the left in this figure and passed through the first porous plate 36, still considerably has a leftward velocity component. That is, the effect of paralleling the directions of the flow of the cooling air to the upward direction is relatively smaller. Meanwhile, in Cases 2 to 5 (the thickness ratio is 0.7 to 1.6), the cooling air having passed through the first porous plate 36 flows in the upward direction substantially well, though in some of the cases, the flow of the cooling air having passed through the first porous plate 36 still has a leftward velocity component a little. Particularly in Cases 3 to 5 where the thickness ratio of the first porous plate 36 is not less than 0.8, the effect of the flow adjustment was significant.
The above result shows that when the thickness ratio of the first porous plate 36 is not less than 0.7 (more preferably not less than 0.8) and not more than 1.6, the effect of adjusting the flow of the cooling air to the upward direction by the first porous plate 36 is enhanced, and finally the effect of adjusting the flow of the cooling air having passed through the second porous plate 37 is further enhanced. This finding conforms to the fact that among Cases A, D, and E of Table 1 in each of which the effect of the flow adjustment is larger, the dispersion in velocity is significantly reduced particularly in Cases A and E in each of which the thickness ratio of the first porous plate 36 is not less than 0.7 and not more then 1.6.
FIG. 7 is a cross section schematically showing the flow of the cooling air. The flow of the cooling air is schematically illustrated with bold arrows. First, the directions of the flow of the cooling air supplied from the supply portion 30a to the supply passage 35 are substantially paralleled by the first porous plate 36 to the upward direction. As described above, this effect is particularly significant when the thickness ratio of the first porous plate 36 is not less than 0.7 (more preferably not less than 0.8) and not more than 1.6. Further, by designing the porous plates so that the thickness ratio of the second porous plate 37 is smaller than the thickness ratio of the first porous plate 36, the flow rates of the cooling air, the directions of which have been paralleled to the upward direction by the first porous plate 36, are uniformized successfully by the second porous plate 37. As a result, uniformity is achieved with respect to both the direction and flow rate of the cooling air having passed through the second porous plate 37, and this restrains the time variation in the flow of the cooling air entering into the yarn running space 32. Consequently, unevenness in the yarns Y in terms of cooling is restrained, and the yarns Y having good quality are provided.

Finally, the inventors examined how much the physical properties of the yarns Y are actually improved, as compared with the configuration of the single porous plate, when the porous plates are provided and designed so that the thickness ratio of the second porous plate 37 is smaller than the thickness ratio of the first porous plate 36. Table 3 shows its result. It should be noted that CV% stands for the coefficient of variation (CV) expressed in percentage, and indicates the degree of dispersion in values of physical properties. In this test, dispersion in values were obtained, for elongation, strength, U%, and thermal stress of the yarns Y. Note that U% is a percentage representing the degree of unevenness in yarns (USTER coefficient) measured using an USTER yarn unevenness tester produced by Zellweger Uster.

[Table 3]

	Single porous plate		Two porous plates
	First porous plate	Second porous plate	First porous plate	Second porous plate
Plate thickness t [mm]	1.6	-	1.6	1
Hole diameter d [mm]	2	-	2	2
Thickness ratio t/d [-]	0.8	-	0.8	0.5
Porosity [%]	29.6	-	29.6	29.6
Strength CV%	3.12		2.06
Elongation CV%	3.16		1.93
U% CVm (hi)	0.41		0.32
Thermal stress CV%	1.72		1.57

As shown in Table 3, by designing the porous plates so that the thickness ratio of the second porous plate 37 is smaller than the thickness ratio of the first porous plate 36, the dispersion in each physical property of the yarns Y is decreased, and the quality of the yarns Y is improved. This confirms that, by improving the effect of the flow adjustment of the cooling air by the first porous plate 36 and the second porous plate 37, the time variation in the flow of the cooling air entering into each yarn running space 32 is restrained, and finally the quality of the yarns Y is reliably improved.

[Advantageous Effects]

By designing the porous plates so that the thickness ratio of the second porous plate 37 is smaller than the thickness ratio of the first porous plate 36 as is in the present embodiment, uniformity is achieved with respect to the direction of the flow of the cooling air and the flow rate of the cooling air, and thereby the time variation in the flow of the cooling air entering into each yarn running space 32 is effectively restrained. Further, by designing the thickness ratio of the first porous plate 36 to be not less than 0.7 and not more than 1.6, the effect of paralleling the directions of the flow of the cooling air to the upward direction by the first porous plate 36 is improved, and the effect of the flow adjustment as a whole is further improved.
As a porous plate, perforated metal, which is a metal plate processed through punch press, is often used. For this reason, if the thickness ratio (thickness) of the porous plate is too large, the punch press process is difficult, and there is a possibility that the intended porous plate cannot be prepared. Thus, in the present embodiment, the upper limit of the thickness ratio of the first porous plate 36 is defined as 1.2, to easily produce the first porous plate 36 and the second porous plate 37 by punch press. In addition, by designing the thickness ratio of the first porous plate 36 to be not less than 0.8, as described above, the effect of the flow adjustment is further improved. Thus, it is more preferable that the thickness ratio of the first porous plate 36 is not less than 0.8 and not more than 1.2.
Further, in the present embodiment, it is preferable that the porosity of the second porous plate 37 is equal to or larger than the porosity of the first porous plate 36. If the pressure loss (fluid resistance) in the second porous plate 37 is larger than the pressure loss in the first porous plate 36, it is difficult for the cooling air having passed through the first porous plate 36 to smoothly pass through the second porous plate 37, which may hinder the flow of the cooling air. For this reason, the porosity of the second porous plate 37 is designed to be equal to or larger than the porosity of the first porous plate 36. This prevents the pressure loss in the second porous plate 37 from exceeding a predetermined value, to ensure the smooth flow of the cooling air. This is consistent with the fact that the porosity of the second porous plate 37 is equal to or larger than the porosity of the first porous plate 36 in each of Cases A, D, and E in Table 1, in each of which the effect of the flow adjustment was significant.
Furthermore, as is in the present embodiment, it is preferable that the distance between the first porous plate 36 and the second porous plate 37 is not less than 20 mm and not more than 80 mm. If the distance between the first porous plate 36 and the second porous plate 37 is too large, the flow of the cooling air, the directions of which have been adjusted by the first porous plate 36 to be parallel to the upward direction, may be disturbed before reaching the second porous plate 37. Meanwhile, if the distance between the first porous plate 36 and the second porous plate 37 is too small, the flow of the cooling air passing through the first porous plate 36 is likely to be affected by the second porous plate 37, and this may cause unsuccessful flow adjustment by the first porous plate 36. Thus, by defining the distance between the first porous plate 36 and the second porous plate 37 as being not less than 20 mm and not more than 80 mm, the effect of the flow adjustment brought about by the use of the first porous plate 36 and the second porous plate 37 is reliably improved.
Moreover, as is in the present embodiment, it is preferable that the plurality of cooling cylinders 31 are accommodated in the accommodation box 30. In this arrangement, when sets of yarns Y are respectively spun out from the spinnerets 13, the sets of the yarns Y are simultaneously cooled in the respective cooling cylinders 31. When the plurality of cooling cylinders 31 are disposed in the accommodation box 30, the variation in the flow of the cooling air among the different cooling cylinders 31 tends to be larger because the spaces around the cooling cylinder 31 are different in shape from one another. In this regard, according to the present embodiment, such a variation is able to be decreased well.

[Other embodiments]

The present invention is not limited to the embodiment above. Combinations of components of the above embodiment, and various modifications and variations are possible within the scope of the spirit of the invention.
For example, while the above-described embodiment describes the yarn cooler 3 including the plurality of cooling cylinders 31 disposed in the accommodation box 30, it is not essential that the number of the cooling cylinders 31 in the accommodation box 30 is two or more.
Further, while the cooling cylinders 31 are arranged in a staggered arrangement in two rows each extending in the left-right direction in the above-described embodiment, the manner of arrangement of the cooling cylinders 31 is not limited to this. For example, the cooling cylinders 31 may be aligned in a single row extending in the left-right direction, or may be arranged in multiple rows in an arrangement manner other than the staggered arrangement.

Claims

A yarn cooler conf igured to cool a yarn spun out downward from a spinneret, the yarn cooler comprising:
a cooling cylinder provided below the spinneret to be opposed to the spinneret, the cooling cylinder including therein a yarn running space through which the yarn is runnable, an upper peripheral wall of the yarn running space forming a flow adjustment section configured to adjust the flow of cooling air entering into the yarn running space while a lower peripheral wall of the yarn running space forming a impassable section configured to prevent the cooling air from entering into the yarn running space;

an accommodation box accommodating the cooling cylinder, to which box the cooling air is supplied through a supply portion provided at a lower portion of the accommodation box;

a first porous plate disposed in a supply passage where the cooling air supplied through the supply portion flows upward along the impassable section, the first porous plate being configured to adjust the flow of the cooling air; and

a second porous plate disposed above and apart from the first porous plate in the supply passage, the second porous plate being configured to further adjust the flow of the cooling air having been adjusted by the first porous plate,
wherein the thickness ratio of the second porous plate is smaller than the thickness ratio of the first porous plate.
The yarn cooler according to claim 1, wherein the thickness ratio of the first porous plate is not less than 0.7 and not more than 1.6.
The yarn cooler according to claim 2, wherein the thickness ratio of the first porous plate is not less than 0.8 and not more than 1.2.
The yarn cooler according to any one of claims 1 to 3, wherein the average porosity of the second porous plate is equal to or larger than the average porosity of the first porous plate.
The yarn cooler according to any one of claims 1 to 4, wherein the distance between the first porous plate and the second porous plate is not less than 20 mm and not more than 80 mm.
The yarn cooler according to any one of claims 1 to 5, wherein a plurality of the cooling cylinders are accommodated in the accommodation box.