EP0540760B1 - Bobbin holder - Google Patents
Bobbin holder Download PDFInfo
- Publication number
- EP0540760B1 EP0540760B1 EP92910581A EP92910581A EP0540760B1 EP 0540760 B1 EP0540760 B1 EP 0540760B1 EP 92910581 A EP92910581 A EP 92910581A EP 92910581 A EP92910581 A EP 92910581A EP 0540760 B1 EP0540760 B1 EP 0540760B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- bobbin
- roving
- pivot
- bearing
- bobbin holder
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
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Classifications
-
- D—TEXTILES; PAPER
- D01—NATURAL OR MAN-MADE THREADS OR FIBRES; SPINNING
- D01H—SPINNING OR TWISTING
- D01H1/00—Spinning or twisting machines in which the product is wound-up continuously
- D01H1/14—Details
- D01H1/18—Supports for supply packages
- D01H1/183—Overhead suspension devices
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
- B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
- B65H59/00—Adjusting or controlling tension in filamentary material, e.g. for preventing snarling; Applications of tension indicators
- B65H59/10—Adjusting or controlling tension in filamentary material, e.g. for preventing snarling; Applications of tension indicators by devices acting on running material and not associated with supply or take-up devices
- B65H59/16—Braked elements rotated by material
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
- B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
- B65H2701/00—Handled material; Storage means
- B65H2701/30—Handled filamentary material
- B65H2701/31—Textiles threads or artificial strands of filaments
Definitions
- the present invention relates to a bobbin holder. More particularly, it relates to a bobbin holder which is a principal functional part indispensable for roving and spinning processes in a spinning factory.
- a conventional bobbin holder as it is known from US-A-4 111 381 is of the structure wherein a rolling contact bearing structure portion of which the bearing itself is adapted to have a rotating-resistant value of substantially 0 is disposed axially of the bobbin holder; and an adjustable braking mechanism, adapted to make a brake shoe 7Bd (see Fig. 7) press against a rotating part by means of a coiled spring 3Bp separately provided, is provided with the bearing portion.
- the braking-torque b ⁇ k on the bearing side is substantially constant, where b is produced by multiplying the pressing force by a friction coefficient ⁇ ; k is the distance from the rotation center of the rotation part to the point of action of frictional force.
- the roving withdrawing-tension T f with a full bobbin (radius R f) is set at 2.0g
- the roving withdrawing-tension T o with the empty bobbin (radius R o ) amounts up to 6 to 12g, which exposes a defect of going far out of the optimum allowance (3.0 ⁇ 1g.) according to spinning technology.
- a bobbin holder according to the preamble of claim 1 which provides a pivotal arrangement for rotationally supporting a bobbin receiving portion.
- the receiving portion is provided with rockable members spaced apart by constant angle so as to receive and hold the bobbin with its rotational axis being flush or well-centered with the rotational axis of the bobbin holder in order to achieve a uniform distribution of the withdrawing tension in the yarn along the circumference of the bobbin.
- rockable members spaced apart by constant angle so as to receive and hold the bobbin with its rotational axis being flush or well-centered with the rotational axis of the bobbin holder in order to achieve a uniform distribution of the withdrawing tension in the yarn along the circumference of the bobbin.
- the bearing structure according to the invention is capable of constantly and proportionally feeding relaxedly twisted roving at the very limit of allowance, with an appropriate tension for a long period of time. According to reliable data obtained from the group equipped with spindles in a scale of about ten thousand spindles, an expected value of roving withdrawing-tension T in each spindle or between spindles is restricted within the range of 3.0 ⁇ 1.0g throughout all counts of spun yarn and throughout all the kinds of spinning products.
- the present invention is based on a so-called “ thrust bearing method based on sliding-contact” i.e. on a property that the " rotational friction torque B ⁇ K” varies in proportion with an increase or decrease in a load P of rotating part (hereinafter referred to as " roving bobbin weight”), which load consists mainly of the weight of a roving bobbin varying in proportion to the radius R of the roving bobbin.
- roving bobbin weight a load P of rotating part
- the sliding-contact thrust bearing possesses novel features while utilizing the related arts disclosed in Japanese Patents Nos. 996924 and 995381, Japanese Patent Application No. 162304/1984 and the like which are associated with the present invention.
- a bobbin holder comprising a suspended rotor which is rotated by a bobbin-rotating-torque T ⁇ R varying in proportion with variation in the radius of a roving bobbin as the roving is withdrawn from the roving bobbin while suspending the roving bobbin (refer to Fig.
- the suspending mechanism comprises a pivot having a partially conical pivot head formed at least in either of the suspended rotor and the upper structure and an engaging bore formed in the other of the two for engaging with the partially conical pivot head to support the weight P of the suspended rotor (roving bobbin weight) so as to generate a frictional force proportional to the roving bobbin weight P in cooperation with the partially conical pivot head thereby generating a braking-torque B ⁇ K working on the suspended rotor and varying in proportion with an increase or decrease in the roving bobbin weight P proportional to the radius R of the roving bobbin, the bobbin-rotating torque T ⁇ R being well-balanced with the braking-torque B ⁇ K such that a roving withdrawing-tension T always becomes substantially constant.
- the bobbin holder of the present invention is so arranged that at least a portion of a pivot housing constituting the periphery of the engaging bore is made appropriately replaceable so as to enable to alter the bore diameter of the engaging bore as far as the pivot is engageable therewith and/or in a coefficient of friction of the pivot housing constituting the periphery of the engaging bore, whereby the braking-torque B ⁇ K can be variably adjusted.
- a " selective combination (or recombination) mating system” based on an originally-devised semi-cylindrical bearing member which is formed of, a bisected and molded half so that the bore-diameter of the bearing (engaging bore) can be properly altered as far as the pivot member can be engaged therewith, while at the same time the coefficient of friction can be properly selected, whereby a bearing arrangement capable of setting stepwise the braking-torque B ⁇ K of the sliding-contact bearing to a desired level is completed. With the bearing arrangement, a variable setting of the tension of roving being supplied has been attained.
- the ratio of P to R (P/R) can be considered to be substantially constant. Accordingly, throughout the process from when the roving bobbin is full (the radius of the roving bobbin is R f ) to when it is empty (the radius of the roving bobbin is R o ), the roving withdrawing-tension T can be set specific and constant.
- the roving withdrawing-tension T has a so-called " three dimensional relation" with the bore-diameter d of the engaging bore on the bearing side and the friction coefficient ⁇ of the bearing member serving as a parameters.
- a bearing bore-diameter d 1 is to be determined for basically setting a roving withdrawing-tension T 11 on the basis of this graph, a line T 11 -C 11 is drawn parallel to the X-axis from T 11 , and a point of intersection C 11 of the line T 11 -C 11 with an oblique line OB 1 representing a friction coefficient initially selected is orthogonally projected on the X-axis to find the bearing bore-diameter d 1 .
- a line segment d 1 -c 11 is extended to give a line segment d 1 -c 12 , and a point of intersection c 12 of the line segment d 1 -c 12 with an oblique line OB 2 is orthogonally projected on the Y-axis to find a point T 12 which is a roving withdrawing-tension T 12 resulting from the fine adjustment.
- Other adjustments are achieved likewise.
- a space is formed in the periphery of the bearing member, and an originally-devised dustproof band area composed of rotatable and concentrically partitioned spaces is provided in the space for assuredly protecting the bearing function for a long period (10 years or more).
- annular space is formed in the suspending mechanism assuming the axis thereof, which space comprises an upper annular groove formed in a top of an inner wall of the fixing portion of the bobbin holder and a lower annular groove formed in a top end of the suspended rotor which grooves face vertically opposite to each other in a substantially symmetrical relation; and a dustproof cylinder is put freely in the annular space and on the bottom of the lower annular groove thereby substantially isolating the suspending mechanism from the outside of the bobbin holder, both upper and lower portions of which cylinder are overlapped with a clearance remaining in the above-mentioned two grooves.
- the dustproof ring completely embraces the suspending mechanism while concentrically partitioning the annular space into a plurality of spaces.
- this structure possesses an outstanding dustproof effect based on an active dust-collecting phenomenon by interwinding of fly going toward the bearing portion; that is, for example, shown in Fig. 2, fly and dust coming into a peripheral space a gathers other fly to form matted and ball-like-shaped matters having a dust-collecting-effect while a suspended rotor 2A rotates slowly, and most of the ball-like-shaped matters remain in the chamber a with the help of a thin cylinder 401, and the same dust collecting phenomenon as the above also occurs in the next spaces b 1 and b 2 .
- a coiled spring 402 can be mounted in the space to incorporate a braking mechanism for a special purpose into the arrangement of the invention (refer to Fig. 2).
- the upper and lower parallel faces are adaped to effectively serve as friction faces.
- the bobbin holder of the present invention can be provided with connecting means allowing easy doffing and donning, capable of remarkably improving the durability and close fitting property of the connecting portion.
- the rotatable portion of the bobbin holder comprises a suspended body for suspending the bobbin, which suspened rotor has a cylindrical chamber opened in a top end thereof, a substantially cylindrical block fitted into the cylindrical chamber, an annular recess, substantially rectangular in section, of which three sides are formed of a slope formed on the entire outer circumference of the block at the upper edge thereof and a groove of V-shaped section formed on the entire inner circumference of the cylindrical chamber at a location corresponding to the slope, and a C-shaped snap ring resiliently closely fitted into the circular annular recess, whereby the weight of the rotatable portion is uniformly dispersed over the entire circumference of the C-shaped snap ring, while the three parts (the suspended rotor, the block and the C-shaped snap ring) are integrated using the weight of the rotatable portion extremelyly to make the connection secured and close.
- an upper structure 1A comprises an assembled construction wherein a bolt 30 and a thrust bearing (hereinafter referred to as " pivot") 606 are made separate and independent according to a new idea, and coaxially and joinedly housed in a coupler (hereinafter referred to as " pivot housing") 101 comprising an original bearing member composed of bisected and molded halves.
- pivot housing a coupler
- the pivot housing 101 is formed by mating two bisected cylindrical and molded members obtained by splitting a cylindrical member along the axis thereof.
- an upper chamber 11G and an intermediate chamber 10G are coaxially and serially formed.
- the upper chamber 11G accommodates a bolt head 31 fixedly
- the intermediate chamber 10G accomodates rotatably and pivotally the upper end of the pivot 606, or the pivot head 61 shaped to have a conical or a similarly curved surface, whereby a bolt 3A and the pivot 606 are coaxially connected to each other by means of the pivot housing 101.
- the pivot housing 101 is pressed from below to fit into a top cap 102 along the axis y-y of the top cap 102, and further, the top cap 102 and the pivot housing 101 are fastened by means of a bolt 30, a washer 33 and a nut 32 to integrally form the upper structure 1A.
- a lower chamber 12G which is digged in the center of a block 201 disposed on the top of a suspended rotor 2A, accommodates an enlarged bottom base 62 of the pivot 606 along a small window 20H opening extending upwardly and coaxially with the axis y-y.
- the block 201 defining the lower chamber 12G can be of the monolithic type or the bisected type, the latter is preferable in view of effectiveness and convenience in function, molding and assembling.
- the top end face of the lower chamber 12G can be made substantially conical for allowing pivotal movement thereat.
- the bearing structure wherein the lower chamber 12G is made similar in shape to the intermediate chamber 10G; the chambers 12G, 10G share the pivot 606 of which opposite ends are made similar each other in shape; and two rotatable and slidable portions are coaxially disposed one above the other, is optimal for use as the bearing in the bobbin holder BH. That is because either smaller one in generated frictional force of the two rotatable and slidable portions, slides and rotates, and if there occures an increase in the frictional force exerting on the sliding and rotating portion by some reason, the other portion begins to slide and rotate in compensation for the former, thereby maintaining the braking-torque constant.
- Fig. 5 shows an embodiment of an original arrangement for fixedly and closely integrating a predetermined portion of a cylinder 22 formed in the top portion of the suspended rotor 2A with the block 201 fitted into the cylinder 22 from above.
- a conical face G 1 formed on the shoulder of the block 201 and a V-shaped groove 22G formed in the inner wall of the cylinder 22 so as to cross the axis y-y at right angles cooperate to share the lower edge portion G 2 thereof and form an annular recess 22U having a rectangular section (formed of three faces G 1 , G 3 and G 4 ) of which the bottom face G 3 is made to have a width equivalent to the diameter d s of a wire forming a C-shaped snap ring 202 (refer to Fig.
- the C-shaped snap ring 202 originally formed of the wire having the diameter d s has a free outer diameter D c (outer diameter in unforced condition) and is fitted into the annular recess 22U along the inner wall of the cylinder while being bent so as to reduce the free outer diameter D c , whereby a structure wherein the cylinder 22, the block 201 and the C-shaped snap ring 202 are closely integrated each other can be implemented with well-balancing in terms of vectors of the internal force working on the three orthogonally crossed circumferential faces including the two circumferential slopes G 1 and G 4 of the annular recess 22U and the bottom circumferential face G 3 according to statics principle.
- the outer diameter D s of the C-shaped snap ring 202 when fitted into the annular recess 22U is substantially the sum of the inner diameter D H of the cylinder 22 and the wire diameter of the C-shaped snap ring d s and made the same or smaller than the free diameter D c , or D c ⁇ D s ⁇ D H + d s .
- Fig. 6 is a sectional view illustrating a vector distribution of the force derived from the roving bobbin weight P and exerting on the pressure-contacted circumferential faces G 1 , G 3 and G 4 shown in Fig. 5. Specifically, it shows a well-balanced distribution of vector F derived from the roving bobbin weight P in terms of orthogonal coordinate system X-Y passing through the three pressure-contact points P 1 , P 2 and P 3 with the center O of the cross section of the wire forming the C-shaped snap ring 202 assumed as the origin.
- Another internal force F o working on the point O which is derived from the restoring force of the C-shaped snap ring 202 causes the ring 202 to be assuredly closely fitted into the annular recess 22U and will not permit it to come out of the recess 22U even when the roving bobbin weight P of roving is not imposed.
- Fig. 2 shows an embodiment of an originally-arranged dustproof structure in the present invention which exhibits a high effect of preventing entrance of fly and dust toward the bearing.
- the inner top end face of the top cap 102 and the top end face of the suspended rotor 2A face opposite and parallel to each other horizontally.
- the two faces are formed with upper and lower annular grooves 102M and 201M with the axis y-y assuming a center thereof, respectively.
- the two annular grooves 102M and 201M are disposed substantially vertically symmetric so as to define a space around the bearing portion with the pivot 606 assumed as an axis.
- a thin cylinder 401 having a predetermined height for maintaining a gap between a top end of the cylinder 401 and a ceiling of the upper annular groove 102M.
- the upper and lower portions of the cylinder 401 are overlapped remaining a clearance with the upper and lower annular grooves 102M and 201M, respectively.
- the circumferental wall of the thin cylinder 401 slowly rotating in the space around the pivot 606 and the non-rotating wall (inner wall of the top cap 102) facing opposite thereto define concentrically partitioned dustproof spaces a , b 1 , b 2 and c which cause the fly to interwind.
- the dustproof spaces form an annular dustproof band area which encloses the bearing structure and actively prevents from and cuts off the ambient atmosphere by utilizing the interwinding phenomenon of the fly.
- the functional innovation of the bearing portion in the bobbin holder of the present invention contributes to a remarkable improvement of a bobbin holder. That is, it has been verified that dispersion of the roving withdrawing-tension T in a spindle or between spindles is stably confined to the range of ⁇ 0.5g with respect to a specific standard value for a long period (according to practical experiments). Particularly, it is worth noting the results of the invention such that has been realized a safe, sure and stable feeding of extra relaxedly twisted roving and extra fine roving which has heretofore been considered to be practically impossible.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Textile Engineering (AREA)
- Spinning Or Twisting Of Yarns (AREA)
- Unwinding Of Filamentary Materials (AREA)
- Sliding-Contact Bearings (AREA)
- Snaps, Bayonet Connections, Set Pins, And Snap Rings (AREA)
Abstract
Description
- The present invention relates to a bobbin holder. More particularly, it relates to a bobbin holder which is a principal functional part indispensable for roving and spinning processes in a spinning factory.
- A conventional bobbin holder as it is known from US-A-4 111 381 is of the structure wherein a rolling contact bearing structure portion of which the bearing itself is adapted to have a rotating-resistant value of substantially 0 is disposed axially of the bobbin holder; and an adjustable braking mechanism, adapted to make a brake shoe 7Bd (see Fig. 7) press against a rotating part by means of a coiled spring 3Bp separately provided, is provided with the bearing portion. Accordingly, unless the pressing force by the coiled spring is changed, the braking-torque b·k on the bearing side is substantially constant, where b is produced by multiplying the pressing force by a friction coefficient µ ; k is the distance from the rotation center of the rotation part to the point of action of frictional force.
- Thus, in view of the fact that
- As shown in Fig. 7, in the conventional bobbin holder the
space 4B in the periphery of the bearing portion is narrowed by being substantially filled with the bearing structure. Fly involving dust dragged into the space is piled up and up, and finally, leads to a fatal phenomenon and is tightly wound around a pivot member 3Br. Further, reciprocating shock load produced by doffing and donning operation of a bobbin causessteel balls 5B to hit and damage upper andlower raceways - Furtheron, from the document EP-A-0 081 585 a bobbin holder according to the preamble of
claim 1 is known which provides a pivotal arrangement for rotationally supporting a bobbin receiving portion. The receiving portion is provided with rockable members spaced apart by constant angle so as to receive and hold the bobbin with its rotational axis being flush or well-centered with the rotational axis of the bobbin holder in order to achieve a uniform distribution of the withdrawing tension in the yarn along the circumference of the bobbin. One particular disadvantage of this known bobbin holder is seen in that the withdrawing tension of the yarn is fixed once the bobbin holder is manufactured. - Considering the disadvantage of the aforementioned prior art, it is the object of the invention to provide an easily adjustable and durable bobbin holder capable of constantly maintaining the adjusted withdrawing tension in the yarn.
- The object is achieved with a bobbin holder having the features as set forth in
claim 1. - Advantageous modifications of the bobbin holder according to the invention are described by the dependent claims 2 and 3.
- There is a close negative correlation between the twist coefficient of roving being supplied and the drafting characteristic of a spinning machine. Accordingly, for improving and stabilizing the quality of spun yarn the bearing structure according to the invention is capable of constantly and proportionally feeding relaxedly twisted roving at the very limit of allowance, with an appropriate tension for a long period of time. According to reliable data obtained from the group equipped with spindles in a scale of about ten thousand spindles, an expected value of roving withdrawing-tension T in each spindle or between spindles is restricted within the range of 3.0 ± 1.0g throughout all counts of spun yarn and throughout all the kinds of spinning products.
- The present invention is based on a so-called " thrust bearing method based on sliding-contact" i.e. on a property that the " rotational friction torque B·K" varies in proportion with an increase or decrease in a load P of rotating part (hereinafter referred to as " roving bobbin weight"), which load consists mainly of the weight of a roving bobbin varying in proportion to the radius R of the roving bobbin. Further, the sliding-contact thrust bearing possesses novel features while utilizing the related arts disclosed in Japanese Patents Nos. 996924 and 995381, Japanese Patent Application No. 162304/1984 and the like which are associated with the present invention. By virtue of the present invention, a way has been opened for application of a braking property inherent to the sliding-contact thrust bearing of a bobbin holder BH, while a basic system has been accomplished for enhancing the reliability of bearing function of the bobbin holder BH to a high level.
- Thus, according to the present invention there is provided a bobbin holder comprising a suspended rotor which is rotated by a bobbin-rotating-torque T·R varying in proportion with variation in the radius of a roving bobbin as the roving is withdrawn from the roving bobbin while suspending the roving bobbin (refer to Fig. 1), an upper structure for fixing the bobbin holder to a creel bar or the like, and a suspending mechanism for rotatably and pivotally suspending the suspended rotor from the upper structure,
wherein the suspending mechanism comprises a pivot having a partially conical pivot head formed at least in either of the suspended rotor and the upper structure and an engaging bore formed in the other of the two for engaging with the partially conical pivot head to support the weight P of the suspended rotor (roving bobbin weight) so as to generate a frictional force proportional to the roving bobbin weight P in cooperation with the partially conical pivot head thereby generating a braking-torque B·K working on the suspended rotor and varying in proportion with an increase or decrease in the roving bobbin weight P proportional to the radius R of the roving bobbin, the bobbin-rotating torque T·R being well-balanced with the braking-torque B·K such that a roving withdrawing-tension T always becomes substantially constant. - Further, the bobbin holder of the present invention, is so arranged that at least a portion of a pivot housing constituting the periphery of the engaging bore is made appropriately replaceable so as to enable to alter the bore diameter of the engaging bore as far as the pivot is engageable therewith and/or in a coefficient of friction of the pivot housing constituting the periphery of the engaging bore, whereby the braking-torque B·K can be variably adjusted.
- To realize such arrangement, developed is, for example, a " selective combination (or recombination) mating system" based on an originally-devised semi-cylindrical bearing member which is formed of, a bisected and molded half so that the bore-diameter of the bearing (engaging bore) can be properly altered as far as the pivot member can be engaged therewith, while at the same time the coefficient of friction can be properly selected, whereby a bearing arrangement capable of setting stepwise the braking-torque B·K of the sliding-contact bearing to a desired level is completed. With the bearing arrangement, a variable setting of the tension of roving being supplied has been attained.
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- On the other hand, since the roving bobbin weight P continues to decrease gradually in proportion with a gradual decrease in the radius R of the roving bobbin due to withdrawing of the roving, the ratio of P to R (P/R) can be considered to be substantially constant. Accordingly, throughout the process from when the roving bobbin is full (the radius of the roving bobbin is Rf) to when it is empty (the radius of the roving bobbin is Ro), the roving withdrawing-tension T can be set specific and constant.
- In addition to the above function, a means has been realized which is capable of easily and rationally specifying or adjusting the value
- As will be described with reference to Fig. 3, in the bobbin holder of the present invention, the roving withdrawing-tension T has a so-called " three dimensional relation" with the bore-diameter d of the engaging bore on the bearing side and the friction coefficient µ of the bearing member serving as a parameters. Fig. 3 is a schematic diagram showing an example of characteristic graph providing as an aim for setting conditions for functions of the bearing member, wherein an empirical value
- When a bearing bore-diameter d1 is to be determined for basically setting a roving withdrawing-tension T11 on the basis of this graph, a line T11-C11 is drawn parallel to the X-axis from T11, and a point of intersection C11 of the line T11-C11 with an oblique line OB1 representing a friction coefficient initially selected is orthogonally projected on the X-axis to find the bearing bore-diameter d1.
- In turn, when a braking-torque value is to be fine-adjusted by replacing one of the two semi-cylindrical and molded halves sharing the bearing bore thus determined with another one to alter only the braking-torque coefficient inherent to the bearing member from
tanθ 1 to tanθ 2, a line segment d1-c11 is extended to give a line segment d1-c12, and a point of intersection c12 of the line segment d1-c12 with an oblique line OB2 is orthogonally projected on the Y-axis to find a point T12 which is a roving withdrawing-tension T12 resulting from the fine adjustment. Other adjustments are achieved likewise. Thus, as a result of the present invention, a selection system has been prepared and established for arbitrary and stepwise adjustment to keep the roving withdrawing-tension T constant. - Further, in an advantageous embodiment of the present invention, a space is formed in the periphery of the bearing member, and an originally-devised dustproof band area composed of rotatable and concentrically partitioned spaces is provided in the space for assuredly protecting the bearing function for a long period (10 years or more). Specifically, an annular space is formed in the suspending mechanism assuming the axis thereof, which space comprises an upper annular groove formed in a top of an inner wall of the fixing portion of the bobbin holder and a lower annular groove formed in a top end of the suspended rotor which grooves face vertically opposite to each other in a substantially symmetrical relation; and a dustproof cylinder is put freely in the annular space and on the bottom of the lower annular groove thereby substantially isolating the suspending mechanism from the outside of the bobbin holder, both upper and lower portions of which cylinder are overlapped with a clearance remaining in the above-mentioned two grooves. The dustproof ring completely embraces the suspending mechanism while concentrically partitioning the annular space into a plurality of spaces.
- It has been verified that this structure possesses an outstanding dustproof effect based on an active dust-collecting phenomenon by interwinding of fly going toward the bearing portion; that is, for example, shown in Fig. 2, fly and dust coming into a peripheral space a gathers other fly to form matted and ball-like-shaped matters having a dust-collecting-effect while a suspended
rotor 2A rotates slowly, and most of the ball-like-shaped matters remain in the chamber a with the help of athin cylinder 401, and the same dust collecting phenomenon as the above also occurs in the next spaces b1 and b2. - It should be noted that a
coiled spring 402 can be mounted in the space to incorporate a braking mechanism for a special purpose into the arrangement of the invention (refer to Fig. 2). In this case the upper and lower parallel faces are adaped to effectively serve as friction faces. - The bobbin holder of the present invention, can be provided with connecting means allowing easy doffing and donning, capable of remarkably improving the durability and close fitting property of the connecting portion.
- Specifically, in the constitution of the connecting means, the rotatable portion of the bobbin holder comprises a suspended body for suspending the bobbin, which suspened rotor has a cylindrical chamber opened in a top end thereof, a substantially cylindrical block fitted into the cylindrical chamber, an annular recess, substantially rectangular in section, of which three sides are formed of a slope formed on the entire outer circumference of the block at the upper edge thereof and a groove of V-shaped section formed on the entire inner circumference of the cylindrical chamber at a location corresponding to the slope, and a C-shaped snap ring resiliently closely fitted into the circular annular recess, whereby the weight of the rotatable portion is uniformly dispersed over the entire circumference of the C-shaped snap ring, while the three parts (the suspended rotor, the block and the C-shaped snap ring) are integrated using the weight of the rotatable portion exquisitely to make the connection secured and close.
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- Fig. 1 is a sectional view showing an embodiment of a sliding-contact thrust hearing structure in a bobbin holder of the present invention;
- Fig. 2 is a sectional view showing another embodiment of a sliding-contact thrust bearing in a bobbin holder of the present invention, wherein a rotatable isolation band area composed of self-cleaning partitioned chambers, and the pivot shown in Fig. 1 is invertedly provided;
- Fig. 3 is a schematic diagram showing the correlation among roving withdrawing-tension T, bearing bore-diameter d and friction coefficient µ of a bearing member, based on which are set functional conditions associated with the bearing member in the bobbin holder shown in Fig. 1;
- Fig. 4 is a plan view showing an original C-shaped snap ring for use in a bobbin holder of the present invention;
- Fig. 5 is a sectional view showing an example of a integrated structure using the C-shaped snap ring shown in in Fig. 4;
- Fig. 6 is a sectional view for illustrating the vector distribution of the force exerted inside the integrated structure shown in Fig. 5 by the load applied to the rotatable portion and a balanced condition of the vector distribution;
- Fig. 7 is a sectional view showing an example of a conventional bearing arrangement based solely on rolling contact system and provided with a braking mechanism.
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- 1A
- upper structure
- 2A
- suspended rotor
- 3A
- bolt for mounting to a creel
- 4A
- space in the periphery of the bearing
- 61
- pivot head
- 62
- pivot base
- ds
- diameter of a wire forming a snap ring
- DH
- inside diameter of the top portion of a cylinder
- Ds
- operative diameter of a snap ring
- Dc
- free diameter of a snap ring
- T
- roving withdrawing-tension
- d
- bearing bore-diameter
- P
- roving bobbin weight
- F
- internal force
- OB
- braking-torque coefficient (tanθ )
- a, b1, b2 and c
- annular dustproof spaces
- Bb
- bobbin
- BH
- bobbin holder
- Rb
- roving bobbin
- 101
- pivot housing
- 102
- top cap
- 201
- block
- 202
- C-shaped snap ring
- 303
- junction pin
- 401
- thin cylinder
- 402
- brake spring
- 601
- circumferential contacting face
- 606
- pivot
- 10G
- intermediate chamber
- 11G
- upper chamber
- 12G
- lower chamber
- 10H
- small bore of intermediate chamber
- 20H
- small bore of lower chamber
- 20E
- section of a wire forming C-shaped snap ring
- 22G
- V-shaped groove
- 22U
- annular recess
- 102M
- upper annular groove
- 202M
- lower annular groove
- The present invention will be described in detail by way of advantageous embodiments with reference to the drawings.
- Referring to Fig. 1, an
upper structure 1A comprises an assembled construction wherein abolt 30 and a thrust bearing (hereinafter referred to as " pivot") 606 are made separate and independent according to a new idea, and coaxially and joinedly housed in a coupler (hereinafter referred to as " pivot housing") 101 comprising an original bearing member composed of bisected and molded halves. - In detail, the
pivot housing 101 is formed by mating two bisected cylindrical and molded members obtained by splitting a cylindrical member along the axis thereof. In the body of thepivot housing 101, anupper chamber 11G and anintermediate chamber 10G are coaxially and serially formed. Theupper chamber 11G accommodates abolt head 31 fixedly, while theintermediate chamber 10G accomodates rotatably and pivotally the upper end of thepivot 606, or thepivot head 61 shaped to have a conical or a similarly curved surface, whereby abolt 3A and thepivot 606 are coaxially connected to each other by means of thepivot housing 101. Thepivot housing 101 is pressed from below to fit into atop cap 102 along the axis y-y of thetop cap 102, and further, thetop cap 102 and thepivot housing 101 are fastened by means of abolt 30, awasher 33 and anut 32 to integrally form theupper structure 1A. In a lower structure, on the other side, alower chamber 12G, which is digged in the center of ablock 201 disposed on the top of a suspendedrotor 2A, accommodates anenlarged bottom base 62 of thepivot 606 along asmall window 20H opening extending upwardly and coaxially with the axis y-y. When the bobbin holder HB thus constructed is suspended from the creel, the suspendedrotor 2A is completely suspended and held by thepivot 606 thehead 61 of which is embraced by theintermediate chamber 10G of thepivot housing 101, and a frictional force is generated between a circumferential contactingface 601 of the bearing bore having a predetermined bore-diameter d and formed in the center of the bottom of the intermediate chamber and the conical face of thepivot head 61 of thepivot 606, whereby the braking-torque ( - In this case, although the
block 201 defining thelower chamber 12G can be of the monolithic type or the bisected type, the latter is preferable in view of effectiveness and convenience in function, molding and assembling. The top end face of thelower chamber 12G can be made substantially conical for allowing pivotal movement thereat. In addition, it is also possible to form a bearing structure wherein the lower andintermediate chambers 2G, 10G shown in Fig. 1 are inversed as shown in Fig. 2. Otherwise, it has been verified that the bearing structure, wherein thelower chamber 12G is made similar in shape to theintermediate chamber 10G; thechambers pivot 606 of which opposite ends are made similar each other in shape; and two rotatable and slidable portions are coaxially disposed one above the other, is optimal for use as the bearing in the bobbin holder BH. That is because either smaller one in generated frictional force of the two rotatable and slidable portions, slides and rotates, and if there occures an increase in the frictional force exerting on the sliding and rotating portion by some reason, the other portion begins to slide and rotate in compensation for the former, thereby maintaining the braking-torque constant. - Fig. 5 shows an embodiment of an original arrangement for fixedly and closely integrating a predetermined portion of a
cylinder 22 formed in the top portion of the suspendedrotor 2A with theblock 201 fitted into thecylinder 22 from above. A conical face G1 formed on the shoulder of theblock 201 and a V-shapedgroove 22G formed in the inner wall of thecylinder 22 so as to cross the axis y-y at right angles cooperate to share the lower edge portion G2 thereof and form anannular recess 22U having a rectangular section (formed of three faces G1, G3 and G4) of which the bottom face G3 is made to have a width equivalent to the diameter ds of a wire forming a C-shaped snap ring 202 (refer to Fig. 4) to be described later. The C-shapedsnap ring 202 originally formed of the wire having the diameter ds has a free outer diameter Dc (outer diameter in unforced condition) and is fitted into theannular recess 22U along the inner wall of the cylinder while being bent so as to reduce the free outer diameter Dc, whereby a structure wherein thecylinder 22, theblock 201 and the C-shapedsnap ring 202 are closely integrated each other can be implemented with well-balancing in terms of vectors of the internal force working on the three orthogonally crossed circumferential faces including the two circumferential slopes G1 and G4 of theannular recess 22U and the bottom circumferential face G3 according to statics principle. -
- With such structure, a close integration and secured coupling of the suspended
rotor 2A, theblock 201 and the C-shapedsnap ring 202 can be obtained utilizing the roving bobbin weight P. - Fig. 6 is a sectional view illustrating a vector distribution of the force derived from the roving bobbin weight P and exerting on the pressure-contacted circumferential faces G1, G3 and G4 shown in Fig. 5. Specifically, it shows a well-balanced distribution of vector F derived from the roving bobbin weight P in terms of orthogonal coordinate system X-Y passing through the three pressure-contact points P1, P2 and P3 with the center O of the cross section of the wire forming the C-shaped
snap ring 202 assumed as the origin. Another internal force Fo working on the point O which is derived from the restoring force of the C-shapedsnap ring 202 causes thering 202 to be assuredly closely fitted into theannular recess 22U and will not permit it to come out of therecess 22U even when the roving bobbin weight P of roving is not imposed. - Fig. 2 shows an embodiment of an originally-arranged dustproof structure in the present invention which exhibits a high effect of preventing entrance of fly and dust toward the bearing. The inner top end face of the
top cap 102 and the top end face of the suspendedrotor 2A face opposite and parallel to each other horizontally. The two faces are formed with upper and lowerannular grooves annular grooves pivot 606 assumed as an axis. In the space, there is freely put athin cylinder 401 having a predetermined height for maintaining a gap between a top end of thecylinder 401 and a ceiling of the upperannular groove 102M. Thereby, the upper and lower portions of thecylinder 401 are overlapped remaining a clearance with the upper and lowerannular grooves thin cylinder 401 slowly rotating in the space around thepivot 606 and the non-rotating wall (inner wall of the top cap 102) facing opposite thereto define concentrically partitioned dustproof spaces a, b1, b2 and c which cause the fly to interwind. The dustproof spaces form an annular dustproof band area which encloses the bearing structure and actively prevents from and cuts off the ambient atmosphere by utilizing the interwinding phenomenon of the fly. - The functional innovation of the bearing portion in the bobbin holder of the present invention contributes to a remarkable improvement of a bobbin holder. That is, it has been verified that dispersion of the roving withdrawing-tension T in a spindle or between spindles is stably confined to the range of ± 0.5g with respect to a specific standard value for a long period (according to practical experiments). Particularly, it is worth noting the results of the invention such that has been realized a safe, sure and stable feeding of extra relaxedly twisted roving and extra fine roving which has heretofore been considered to be practically impossible.
- In pursuit of steadily matching with the progress of rationalization of a equipment in spinning factories such as larger package, higher speed, further automatization, further continuous operations and so forth, the present invenion further improves the quality of yarn, stabilizes the operations and enhances the serviceability of new equipement. More specifically speaking,
- (1) It has practically been verified that the present invention enables to prolong the effective life of a bearing to a very long period by a remarkably enhanced bearing capability for load, highly improved durability, increased reliability and safety to a marked level, and an excellent tenacity along with a restorability against operational shock load to a bobbin;
- (2) A bobbin holder of " maintenance free" for a long period (15 years or more) has been realized by additionally providing an orignally-devised superior fly proof structure to avoid fatal deterioration of hearing functions;
- (3) Roving withdrawing-tension control in a factory can be completely intensified by rationally optimizing the roving withdrawing-tension T with ease as well as by the previous items (1) and (2);
- (4) Indefinite contribution to cost reduction has been made by rationalizing and simplfying the bearing arrangement thereby promoting normalization and standardization for more general purposes, as well as by enabling automatization of assembly of parts;
- (5) The integrated structure by means of an originally-devised C-shaped snap ring possesses load dispersing effect based on the balance of force and is hence far superior in all properties such as load characteristic, durability as well as convenience, safety and reliability to a conventional structure by means of
pin 303, calking or the like. Therefore, it is expected from now on to be applied to general industrial fields, particularly to a plastic molding field broadly; and - (6) The results of the present invention are not limited to the application herein described, and can be widely utilized as a precise bearing for special purpose in general industrial machines or devices (electronic devices, especially).
Claims (3)
- A bobbin holder comprising a suspended rotor (2A) which is rotated by a bobbin rotating torque (T·R) varying in proportion with a variation in the outer diameter of a roving bobbin (Rb) as the roving is withdrawn from the roving bobbin while suspending the bobbin, and an upper structure (1A) for setting the bobbin holder to a suspension creel and for rotatably and pivotally suspending said suspended rotor (2A), said upper structure (1A) or said suspended rotor (2A) comprising a pivot (606) having at least one partially conical pivot head (61) formed in at least said suspended rotor (2A) or said upper structure (1A), and an engaging bore (10H) for engaging with said pivot head (61) for supporting said suspended rotor (2A), such that the weight (P) of said roving bobbin (Rb) generates a frictional force at said pivot (606) proportional to the weight (P), thereby generating a braking torque (B·K) acting on said suspended rotor (2A) proportionally to an increase or decrease in the weight (P) proportional to the radius (R) of said roving bobbin (Rb), characterized in that at least a portion of a pivot housing (101) constituing the periphery of said engaging bore (10H) is adapted to be easily replaceable so as to enable alteration or adjustment of a bore diameter (d) of said engaging bore (10H) and/or a coefficient of friction (µ) of the member constituing the periphery of the engaging bore (10H), so as to balance a bobbin rotating torque (R·T) with said braking torque (B·K) such that a roving withdrawing tension (T) is made substantially constant.
- A bobbin holder according to claim 1, wherein an annular space (4A) having an axis determined by said suspended rotor (2A) is defined by an upper annular groove (102 M) formed in a top inner wall (102) of said upper structure (1A) and a lower annular groove (202 M) formed in a top end face of said suspended rotor (2A), said grooves (102 M, 202 M) facing each other in a substantially symmetrical relation, and wherein a thin cylinder (401) is movably received in said grooves (102 M, 202 M) with edges thereof overlapping said thin cylinder (401) which completely embraces the pivot mechanism (606, 61, 10H) for substantially dustproofly sealing said pivot mechanism from the outside of said bobbin holder, said thin cylinder (401) being received in said grooves (102 M, 202 M) with a clearance so as to divide said annular spaces defined by said grooves (102 M, 202 M) into a plurality of annular spaces.
- A bobbin holder according to claim 1, wherein said suspended rotor (2A) comprises a suspended cylinder (22) for receiving said bobbin (Rb), said cylinder (22) having a cylindrical chamber open to a top end face thereof and a substantially cylindrical block (201) fitted in said cylindrical chamber having an annular recess (22 U) substantially rectangular in section, three sides (G1, G3, G4) of which being defined by a conical face (G1) formed at an upper shoulder of said block (201) and a V-shaped groove (22 G) formed at an inner circumference of said cylindrical chamber at a location coincident to said conical face (G1), and a C-shaped snap ring (202) resiliently fitted into said annular recess (22 U).
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP145353/91 | 1991-05-21 | ||
JP3145353A JP2545004B2 (en) | 1991-05-21 | 1991-05-21 | Thrust bearing structure in bobbin holder |
PCT/JP1992/000667 WO1992020845A1 (en) | 1991-05-21 | 1992-05-20 | Bobbin holder |
Publications (3)
Publication Number | Publication Date |
---|---|
EP0540760A1 EP0540760A1 (en) | 1993-05-12 |
EP0540760A4 EP0540760A4 (en) | 1993-10-13 |
EP0540760B1 true EP0540760B1 (en) | 1996-09-11 |
Family
ID=15383235
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP92910581A Expired - Lifetime EP0540760B1 (en) | 1991-05-21 | 1992-05-20 | Bobbin holder |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP0540760B1 (en) |
JP (1) | JP2545004B2 (en) |
DE (1) | DE69213652T2 (en) |
HK (1) | HK40397A (en) |
WO (1) | WO1992020845A1 (en) |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH05155434A (en) * | 1991-12-09 | 1993-06-22 | Funai Electric Co Ltd | Pusher device for article conveying system |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5429625B2 (en) * | 1973-08-23 | 1979-09-25 | ||
JPS5111923A (en) * | 1974-07-18 | 1976-01-30 | Zenzaburo Tsukumo | SUICHOKUKENGASOCHI |
JPS5155434A (en) * | 1974-11-09 | 1976-05-15 | Toyo Bearing Mfg Co | |
JPS5928508B2 (en) * | 1976-01-17 | 1984-07-13 | エヌ・テ−・エヌ東洋ベアリング株式会社 | vertical suspension system |
JPS5349863U (en) * | 1976-09-30 | 1978-04-27 | ||
DE3176736D1 (en) * | 1981-06-16 | 1988-06-16 | Zenzaburo Tsukumo | Bobbin holder |
JPS60148870A (en) * | 1984-07-31 | 1985-08-06 | Zenzaburo Tsukumo | Bearing structure of bobbin holder |
-
1991
- 1991-05-21 JP JP3145353A patent/JP2545004B2/en not_active Expired - Lifetime
-
1992
- 1992-05-20 EP EP92910581A patent/EP0540760B1/en not_active Expired - Lifetime
- 1992-05-20 DE DE69213652T patent/DE69213652T2/en not_active Expired - Fee Related
- 1992-05-20 WO PCT/JP1992/000667 patent/WO1992020845A1/en active IP Right Grant
-
1997
- 1997-04-03 HK HK40397A patent/HK40397A/en not_active IP Right Cessation
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH05155434A (en) * | 1991-12-09 | 1993-06-22 | Funai Electric Co Ltd | Pusher device for article conveying system |
Also Published As
Publication number | Publication date |
---|---|
EP0540760A4 (en) | 1993-10-13 |
HK40397A (en) | 1997-04-11 |
JP2545004B2 (en) | 1996-10-16 |
EP0540760A1 (en) | 1993-05-12 |
JPH04343719A (en) | 1992-11-30 |
DE69213652D1 (en) | 1996-10-17 |
DE69213652T2 (en) | 1997-02-13 |
WO1992020845A1 (en) | 1992-11-26 |
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