BOBBIN HOLDER

Abstract: A bobbin holder in such a structure that tension to draw the roving can be kept constant by employing a slide bearing system, while noticing that bobbin-turning torque required for drawing the roving and roving bobbin load are proportional to the radius of the roving bobbin, so that braking torque (in equilibrium with torque for turning the bobbin) to act on the bobbin may consist of a friction force on the basis of weight of the roving bobbin and said braking torque may be variably adjusted with the bore diameter of said bearing and (or) frictional coefficient changed for combination, wherein major components are a narrow window opening (10H) as a bearing hole of a pivot housing (101) provided on the fixed part of the bobbin holder (BH) and a pivot (606) as a shaft for supporting the weight of the rotating part including a roving bobbin (Rb) and lying around said small opening (10H), in which the pivot housing (101) is in the shape of, for example, a cylinder equally divided into two segments each capable of being changed for combination.

Description: TECHNICAL FIELD 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. BACKGROUND ART 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 T·R = b·k , or the braking-torque b·k on the bearing side maintains a close equivalence to the rotating-torque R·T on the roving bobbin side, which exerts on the rotating part as roving is withdrawn, the roving withdrawing-tension T increases in inverse proportion to a decrease in the outer radius R of a roving bobbin due to withdrawing of roving. This results in the so-called "two dimensional relation" between T and R. Practically, with roving bobbins now available, the radius R f of a full bobbin is 3 to 6 times larger than the radius R o of the empty bobbin. Accordingly, even if 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. 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 causes steel balls 5B to hit and damage upper and lower raceways 22R and 35R, and the damage progresses every time the doffing and donning operation of a bobbin is carried out. Thus, the factors accounting for a fatal defect acts synergetically, and a braking-torque is increased from the value initially set, resulting in a noticeable and continuous rise in the braking-torque b·k on the bearing side in an unexpectedly short period (1 to 2 years). This leads to an extreme reduction in effective life of the bobbin holder BH and to a sharp increase in problems which are fatal to both the quality of yarn and the productive operation. Therefore, it is presently impossible to automatize production steps, make them continuous and obtain finer and higher-grade yarn. 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. DISCLOSURE OF THE INVENTION 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. According to Couloms' law, the braking-torque B·K in the " sliding-contact thrust bearing" of the present invention is represented by the following equation (1): B·K = P·d/2· µ Further, since the rotating torque T·R applied to the rotatable portion because of withdrawing of the roving from the surface of the roving bobbin Bb having radius R (refer to Fig. 1) maintains a perfect equilibrium with the braking-torque B·K, the following equation (2) is valid: T·R = P·d/2· µ Here, making the value d/2· µ constant (hereinafter referred to as " resistance coefficient K" ) leads to the following equation (3) with respect to the roving withdrawing-tension T: T = P/R·K 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 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. In addition to the above function, a means has been realized which is capable of easily and rationally specifying or adjusting the value K (K = d/2· µ ) in the equation (3) for setting the roving withdrawing-tension T to a desired value by providing a bearing member having a bore-diameter d of the engaging bore of the bearing side which can be altered within the range allowing engagement with the pivot member having a predetermined diameter, and a friction coefficient µ inherent to the bearing member, for example, semi-cylindrical and molded halves having the same bore-diameter d and same or different friction coefficient µ . 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 " braking-torque coefficient OB (OB = tan = P/R· µ )" is represented in a coordinate system in which bore-diameter d of the bearing member is represented in terms of X-axis while the roving withdrawing-tension T is represented in term of Y-axis. When 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 . 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 tan 1 to tan 2, 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. 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 a thin cylinder 401, and the same dust collecting phenomenon as the above also occurs in the next spaces b 1 and b 2 . 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. BRIEF EXPLANATION OF THE DRAWINGS 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. DENOTATION OF NUMERALS 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 d s diameter of a wire forming a snap ring D H inside diameter of the top portion of a cylinder D s operative diameter of a snap ring D c 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 (tan ) a , b 1 , b 2 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 BEST MODE FOR EFFECTING THE INVENTION 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 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. 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 the pivot housing 101, an upper chamber 11G and an intermediate chamber 10G are coaxially and serially formed. The upper chamber 11G accommodates a bolt head 31 fixedly, while 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. In a lower structure, on the other side, 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. When the bobbin holder HB thus constructed is suspended from the creel, the suspended rotor 2A is completely suspended and held by the pivot 606 the head 61 of which is embraced by the intermediate chamber 10G of the pivot housing 101, and a frictional force is generated between a circumferential contacting face 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 the pivot head 61 of the pivot 606, whereby the braking-torque ( B·K = P·d/2· µ ) which is inherent to " sliding-contact bearing structure", completely works. In this case, although 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. In addition, it is also possible to form a bearing structure wherein the lower and intermediate chambers 2G, 10G shown in Fig. 1 are inversed as shown in Fig. 2. Otherwise, it has been verified that 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. 4) to be described later. 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 . With such structure, a close integration and secured coupling of the suspended rotor 2A, the block 201 and the C-shaped snap 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 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. In the space, there is freely put 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. Thereby, 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. APPLICABILITY TO INDUSTRY 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: 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 (G 1 , G 3 , G 4 ) 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 (G 1 ), and a C-shaped snap ring (202) resiliently fitted into said annular recess (22 U).

Inventors: TSUKUMO SHINSUKE, TSUKUMO ZENZABURO, TSUKUMO, SHINSUKE, TSUKUMO, ZENZABURO, TSUKUMO, SHINSUKE, 4-5, FURUEDAI 2-CHOME, TSUKUMO, ZENZABURO, 4-5, FURUEDAI 2-CHOME
Applicants: ZEN GIKEN CO LTD, ZEN GIKEN CO., LTD.
Application year: 1992
Main classification: B65H49
IPC codes: F16B21, B65H49, B65H59, F16C17, D01H1