US3753517A - Guide roll for filaments - Google Patents

Guide roll for filaments Download PDF

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Publication number
US3753517A
US3753517A US00289316A US3753517DA US3753517A US 3753517 A US3753517 A US 3753517A US 00289316 A US00289316 A US 00289316A US 3753517D A US3753517D A US 3753517DA US 3753517 A US3753517 A US 3753517A
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United States
Prior art keywords
shaft
orifices
flanges
guide roll
provisions
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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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US00289316A
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English (en)
Inventor
Y Takenaka
H Aoyama
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Teijin Ltd
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Teijin Ltd
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Filing date
Publication date
Priority claimed from JP11097671U external-priority patent/JPS5035127Y2/ja
Priority claimed from JP3490772A external-priority patent/JPS48103837A/ja
Application filed by Teijin Ltd filed Critical Teijin Ltd
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Publication of US3753517A publication Critical patent/US3753517A/en
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Expired - Lifetime legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
    • F16C32/0681—Construction or mounting aspects of hydrostatic bearings, for exclusively rotary movement, related to the direction of load
    • F16C32/0696—Construction or mounting aspects of hydrostatic bearings, for exclusively rotary movement, related to the direction of load for both radial and axial load
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H51/00—Forwarding filamentary material
    • B65H51/02—Rotary devices, e.g. with helical forwarding surfaces
    • B65H51/04—Rollers, pulleys, capstans, or intermeshing rotary elements
    • B65H51/06—Rollers, pulleys, capstans, or intermeshing rotary elements arranged to operate singly
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H57/00—Guides for filamentary materials; Supports therefor
    • B65H57/14—Pulleys, rollers, or rotary bars
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C13/00—Rolls, drums, discs, or the like; Bearings or mountings therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C13/00—Rolls, drums, discs, or the like; Bearings or mountings therefor
    • F16C13/02—Bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
    • 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

  • ABSTRACT provides a guide roll for filaments as used in apparatuses in which the draw-twisting, drawwinding, false twisting or heat treatment of the synthetic filaments and the like are carried out, and this guide roll is particularly devised to meet the requirements of high speed operation Again, it can be used under conditions of elevated temperature and high humidity.
  • radial ball bearings have been used in the guide rolls of low speed rotation, but to meet the demands for an increase in the production in recent years guide rolls equipped with fluid bearings are now being used in view of their low torque and ability to endure its high speed operation.
  • This invention concerns a guide roll equipped with this type of fluid bearing and is one whose performance has been enhanced by specifying as to its basic factors, with a mathematical formula, as a result of detailed observations and repeated experimentation, the numerical values involved in its designing, and also through elaborate works in the detailed parts of the fluid bearing, by eliminating the points which might become causes for trouble.
  • the guide roll according to the present invention not only meets the conditions for high speed operation but also can maintain its high performance.
  • This invention relates to a guide roll which is conjointly used with the apparatuses that are used in the manufacturer of synthetic fibers and the like, e.g., draw-twisting machines, the draw-winding machines, false twisting machines or filament heat-treatment machines.
  • this guide roll is used in the following manner.
  • the freshly spun, undrawn filaments are usually submitted to drawing and heat treatments to enhance their properties.
  • the drawing is usually carried out by running the filament between a low speed feed roll and a draw roll having a higher speed than said feed roll. It is desired in this case that the ratio of the filament speed around the feed roll to the speed around the draw roll be maintained constant. That is, the foregoing condition is highly important for obtaining filaments having uniform properties.
  • guide rolls were heretofore provided adjunctly in the vicinities of respectively the feed and draw rolls, and the filament being treated is wound around these rolls several times before being sent to the following steps of such as twisting or winding.
  • the guide roll usually is small and light in weight, its diameter being 20 50 millimeters. It is rotatably mounted on a shaft with a light rotating torque by means of two radial ball bearings, one end of the shaft being affixed to the machine frame, and torque is imparted to the roll by the traveling filament.
  • a relatively low rotational speed In the case of the speeds with which the filaments were treated higher to the speed of the guide roll was of the order of 5000 15,000 rpm, a relatively low rotational speed. Hence, the torque required for starting the guide roll did not cause any difficulty in stringing up the filament. Further, the yarn properties were not impaired by the reaction of the torque imparted to the guide roll by the traveling filament.
  • the fluid bearing e.g., an air bearing
  • the bearing portion comprises a porous sleeve inserted in the journal clearance, into which sleeve pressurized air is introduced.
  • the amount of fluid consumed is less than the other types, e.g., the hearing which uses orifices.
  • the guide roll which is of a diameter of 20 50 millimeters, is usually mounted rotatably with a light rotating torque to a shaft, the one end of which shaft is affixed to the machine frame.
  • the guide roll which is of a diameter of 20 50 millimeters, is usually mounted rotatably with a light rotating torque to a shaft, the one end of which shaft is affixed to the machine frame.
  • the first object resides in obtaining a stable air bearing having a greater load capacity per unit amount of air consumed.
  • the second object resides in obtaining a guide roll for filaments, which possesses stability in respect of the following point.
  • the guide roll using an air bearing as previously noted, undoubtly is improved in its ability to withstand operation at high speeds, heat resistance and lower torque.
  • the object in this case is to solve this drawback and provide a stable guide roll.
  • the third object of the invention resides in providing solutions to the following problems.
  • the air bearing is essentially readily affected greatly by external conditions. For instance, when filaments and like enter the bearing clearance at the time the filament is being strung up, seizure of the bearing takes place instantaneously to cause not only the breakage of the filament but also results in the bearing itself becoming no longer usable. The solution of this point must be achieved. Again, when the filament has been subjected to an excessive load by means of other shafts during the treatment of the filament, or in the case whre the broken filament gets twisted about between the main roll and the guide roll, it is well known from experience that in these cases the filament, which makes several turns about the roll, tend to shift to the rear part of the roll as a result of the pitch of the filament becoming irregular. In case such as this, the chances of the filament entering the bearing clearance of the air bearing increase to cause various troubles such as described above. This also must be solved.
  • the present invention is directed to a guide roll for filaments comprising a roll body fitted rotatably about a shaft, said shaft being provided with orifices through which pressurized air is introduced to form between said roll body and said shaft an air film by which the roll body is supported, characterized in that the air bearing is so designed that the various values involved in its design are chosen such as to satisfy the following relationship wherein n is the total number of orifices for the introduction of the pressurized air, with the limitation that n 6,
  • d is the diameter (mm) of the orifices for introducing the pressurized air
  • Ps is the pressure (kg/cm absolute) at which the pressurized air is fed, with the limitation that Ps C is the clearance (mm) between the roll body and the shaft in the radial direction, with the limitation that C 10 X 10*,
  • D is the outside diameter (mm) of the shaft
  • L is the sum of the distances (mm) from the several orifices to thepressurized airdischarge outlet measured in the axial direction, provided that when there is no pressurized air discharge outlet between adjacent orifices, the distance between said orifices is not included.
  • FIG. 1 is a section view illustrating a guide roll for filaments in accordance with the present invention
  • FIGS. 2, 3 and 4 being respectively sectional views taken along lines ll II, III Ill and 1V IV of FIG. 1
  • FIG. 5 is sectional view illustrating another embodiment of the invention
  • FIG. 6 being a sectional view taken along line VI VI of FIG. 5
  • FIG. 7 is a sectional view showing a still another embodiment of the invention
  • FIG. 8 being a sectional view taken along line VIII VIII of FIG. 7
  • FIG. 9 is a graph showing the relationship between Ps and F.
  • reference numeral 1 is a cylindrical roll body of the filament guide roll, while 2 is a shaft about which the roll body 1 is rotatably fitted to form a clearance 8 between the shaft and the roll body.
  • the shaft 2 is provided with an air passage 5 through its axial center for the introduction of the pressurized air, and branching from the air passage 5 are provided in the shaft 2 orifices 6 from whence the pressurized air is introduced to the clearance 8 to form therein an air film by which the roll body 1 is supported.
  • At the proximal portion of the shaft 2 there is formed integrally thereof a flange 3, while at the other end of the shaft 2 there is screwably attached a flange 7 to the threaded portion 4 of the shaft 2.
  • the shaft 2 is also provided with recessed portions 10 at portions of the shaft intermediately of the orifices 6, the communication between these recessed portions 10 and with the outside being achieved by the provision of holes 11, whereby a part of the pressurized air is discharged to the outside.
  • the flanges 3 and 7 are also provided with orifices 12, which are disposed in the flanges 3 and 7 at positions on an extention line from the air film formed by the clearance between the roll body 1 and the shaft 2.
  • the orifices 12 are also provided for discharging the pressurized air.
  • the flanges 3 and 7 are further provided with sleeves 14, which are so formed such as to envelope the ends of the roll body 1 and by projecting axially of the roll body form clearances between themselves and the roll body 1.
  • the sleeve 14 may be provided at the flange 3 only.
  • R W/Q where R is the load capacity per unit amount of air consumed (kg-min/Nl),
  • W is the radial load capacity (kg) and Q is the amount of air consumed (NI/min).
  • an R value of greater than 0.04 is to be preferred.
  • the load capacity is relatively small as compared with the amount of air consumed, and hence the efficiency of the bearing is very poor.
  • the performance of the air bearing of the present invention was judged for the most part on the basis of the foregoing value. Part of the results of measurements made for determining the range of F are shown in FIG. 9. In the figure the pressure of the air used is represented as abscissa and and F value is represented as ordinate.
  • the bearings tested were of the same type in which values of n, d, L and D were constant but the value of C was varied. The values of C and the reference numerals in the figure correspond as follows:
  • the guide roll Since, in this case, the guide roll is extremely weak in coping with the fluctuations in the pressure at which the pressurized air is fed or fluctuations in the load imposed on the roll, its reliability as a roll for treating high speed filaments declines to make it unsuitable for use in high speed operations. While it is undesirable for the clearance C between the roll body 1 and shaft 2 in the radial direction to be excessively great, there is also a limit to its smallness. For instance, from the standpoint of the processing precision that can be achieved by the present state of the art, it is extremely difficult to make this clearance less than 10 X 10 (mm). There would be decline in the yield at the time of the manufacture of the roll, or the interchangeability of the roll body 1 and the shaft 2 should suffer. Hence, it would be economically disadvantageous, and thus such a small clearance cannot be adopted as a practical matter.
  • the flanges 3 and 7 at the ends of the guide roll are provided with sleeves l4 axially of the roll.
  • the provision of such sleeves l4 prevents the filament being treated from entering the clearance 9 at, say, the time the filament is being strung up. Further, even at those times when the filament breaks between a roll and the guide roll, and the filament shifts towards the rear end of the roll as a result of the filament pitch becoming irregular, the filament does not enter the clearance 9.
  • the recessed portions 10 provided in the shaft 2 are in communication with each other and with the outside by means of holes 11, through which a part of the pressurized air is discharged externally of the guide roll. As a result of the presence of this passage, the discharge of the pressurized fluid is improved, with the consequence that the load capacity of the bearing is increased.
  • the flanges 3 and 7 are prov vided with a plurality of orifices 12.
  • the total effective discharge area of these discharge orifices 12 should be 200 percent of the total area of the orifices 6.
  • the total effective discharge area of the orifices I2 is made about 40 percent of the total area of the orifices 6, it was confirmed that the amount of fluid discharged from the orifices 12 was insufficient, and hence the oscillations set up in the roll body 1 could not be checked.
  • the total effective discharge area of the orifices 12 is made about 230 percent, the amount of fluid discharged from the orifices 12 becomes excessive and likewise the oscillations set up in the roll body could not be checked.
  • EXAMPLE 1 This example illustrates the instance where a bearing having a triple file air feed setup has been used, the various values of the bearing being as follows:
  • an R value of at least 0.04, as obtained by the foregoing method of calculation, is preferred. If the R value is less than this, the load capacity as compared with its amount of air consumed is small, and hence such a bearing has a very poor efficiency. Therefore, the bearing of the present example was deemed to be one of good efficiency. It is believed to be appropriate from the economic and performance standpoints to compare by means of the magnitude of such an R value the performance of the bearing portion which functions as an important part of the roll. When the P value, i.e., log n'd'L/Ps'C 'D, was calculated in this case, it was 4.4. Further, even when the filament guide roll part or the fittings were subjected to shocks, the guide roll was stable, there being no abnormal oscillations in the axial direction.
  • the ratio of the effective discharge area to the total area of the orifices 6 for introducing the pressurized air was H 1r/4 -m (d) -/1r/4 n d 139 percent.
  • EXAMPLE 3 In this example, there i is illustrated the instance where the guide roll used is one having the double file air feed setup.
  • the P value was 3.255. Further, the H value was 84 percent and there was no abnormal oscillations in the axial direction. And even though the fittings, r011 body, etc., were subjected to shocks, oscillations set up would promptly dampen and no troubles were noted. Further, since, as in Example 1, the flanges 3 and 7 at the two ends of the filament guide roll were provided with sleeves in the axial direction, as shown in H6. 5, the effect of preventing the entry of the filament into the clearance, as previously noted, was demonstrated even when the filament was being strung up or when break age of the filament took place. Thus, this guide roll was stable.
  • EXAMPLE 4 Another instance of a guide roll having the same type of double file air feed setup as in the case with Example 3 will be illustrated.
  • Example 5 This example will illustrate the instance of a guide roll having the single file air feed setup shown in FIG. 7.
  • the R value in this case was 0.139. Since R 0.04, this bearing can be regarded as being efficient.
  • the F value was 3.
  • the bearing was of poor efficiency, as indicated above, because of the excessive magnitude of the clearance C.
  • the F value was measured in this case, it was 1.944.
  • the guide roll of the present invention excels in its efficiency of load capacity per unit amount of air consumed, and hence is a roll that is stable economically and performance wise. Further, according to the present invention, when abnormal oscillations are set up in the roll body 1 in the axial direction and the end of the roll body 1 and the flange 7 come into contact to cause the clearance 9 to disappear, the pressurized air is not discharged from the clearance 9 but is discharged only from the discharge orifices 12 of the flange 7, since orifices 12 are provided on an extension line from the air film.
  • the filament does not make entry into the clearance 9 even when breakage of the filament, etc., occur.
  • a filament guide roll excelling in stability and operability can be provided.
  • the entry of the filament into the clearance 13 between the roll body 1 and the sleeve 14 is more effectively prevented as the clerarance 13 becomes smaller, but if this clearance is too small, the act of throttling the discharge of the pressurized air takes place to cause a decline in the performance of the air bearing at the clearances 8 and 9.
  • the clearance 13 is to be determined as a result of various tests, in accordance with our experiences, the end can be achieved without preventing the discharge of the pressurized air and without impairing the effect of preventing the entry of the filament, if the clearance 13 is made of a magnitude several tens of times that of the bearing clearances 8 and 9. Further, it goes without saying that it is also possible to reduce the clearance 13 still more if the pressurized air, which has passed through the bearing clearance 9, is not discharged via the clearance 13 axially of the roll body 1 but is discharged radially of the roll body by providing, say, discharge orifices in the peripheral surface of the sleeve 14.
  • the sleeve 14 can fully demonstrate its effectiveness in preventing the entry of the filament if it overlaps the roll body 1 axially thereof for several millimeters.
  • the present invention can be applied to all filament guide rolls which use orifices as the throttle, there being no restrictions imposed for the reason that the bearing used a single file or multifile air feed setup.
  • a guide roll for filaments comprising a roll body fitted rotatably about a shaft, said shaft being provided with orifices through which pressurized air is intro quizzed to form between said roll body and said shaft an air film to thereby provide a bearing means by which the roll body is supported, characterized in that the various values involved in the design of said bearing means, are chosen such as to satisfy the following relationship:
  • n is the total number of orifices for the introduction of the pressurized air, with the limitation that n g 6,
  • d is the diameter in millimeters of the orifices for introducing the pressurized air
  • Ps is the pressure in kilograms per square centimeter absolute at which the pressurized air is fed, with the limitation that Rs 2 3,
  • C is the clearance in millimeters between the roll body and the shaft in the radial direction, with the limitation that C 10 X 10 D is the outside diameter in millimeters of the shaft,
  • L is the sum of the distances in millimeters from the several orifices to the pressurized air discharge outlet measured in the axial direction, provided that when there is no pressurized air outlet between adjace nt orifices, the distance between said orifices is not included.
  • a guide roll according to claim 1, the provisions of one or more holes 11 disposed in said shaft 2 axially thereof, said holes communicating with recessed portions 10 provided inside said shaft 2 at points intermediately of said orifices 6, as well as with the outside of said shaft, and moreover the provisions of flanges 3 and 7 at the ends of said shaft 2, at least one of said flanges being provided with a sleeve 14 extending in the axial direction in such a manner as to envelop the end of the roll body 1.
  • flanges 3 and 7 at the ends of said shaft 2, at least one of said flanges being provided with a sleeve 14 extending in the axial direction in such a manner as to envelop the end of the roll body 1, said flanges 3 and 7 being further provided with a plurality of fluid discharge orifices 12 at positions on the extension line from the clearance 8, the effective discharge area of said discharge orifices 12 being 50 200 percent of the area of said orifices 6.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolls And Other Rotary Bodies (AREA)
US00289316A 1971-11-26 1972-09-15 Guide roll for filaments Expired - Lifetime US3753517A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP11097671U JPS5035127Y2 (de) 1971-11-26 1971-11-26
JP3490772A JPS48103837A (de) 1972-04-07 1972-04-07

Publications (1)

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US3753517A true US3753517A (en) 1973-08-21

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US00289316A Expired - Lifetime US3753517A (en) 1971-11-26 1972-09-15 Guide roll for filaments

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US (1) US3753517A (de)
CA (1) CA962730A (de)
CH (1) CH547222A (de)
DE (1) DE2246903A1 (de)
FR (1) FR2162932A5 (de)
NL (1) NL7213070A (de)

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3986650A (en) * 1974-09-10 1976-10-19 Eastman Kodak Company Positionally constraining web support
US3994193A (en) * 1973-10-01 1976-11-30 Domtar Limited Air bearing slitter
US4098115A (en) * 1976-01-14 1978-07-04 Bayer Aktiengesellschaft Yarn tension measuring device
US4294494A (en) * 1978-12-04 1981-10-13 Hitachi, Ltd. Sliding-type bearing
US4610060A (en) * 1984-08-27 1986-09-09 Eastman Kodak Company Drafting system for yarns
US4759249A (en) * 1985-09-21 1988-07-26 Maschinenfabrik Goebel Gmbh Web slitting apparatus having adjustable lower cutting blades
US5069558A (en) * 1989-11-25 1991-12-03 Fag Kugelfischer Georg Schafer Air-supported laying roller for textile yarn
DE4117388A1 (de) * 1991-05-28 1992-12-03 Koenig & Bauer Ag Walze zum fuehren einer warenbahn
US5224641A (en) * 1990-08-23 1993-07-06 Storage Technology Corporation Air bearing for tape drive
US20080148734A1 (en) * 2004-12-23 2008-06-26 Alstom Technology Ltd Power plant
CN103189659A (zh) * 2010-10-29 2013-07-03 奥依列斯工业株式会社 滚筒装置
WO2013098680A1 (en) * 2011-12-29 2013-07-04 Lakshmi Machine Works Ltd. An improved sliver guide arrangement in a textile machine
CN105386134A (zh) * 2015-12-04 2016-03-09 浙江古纤道新材料股份有限公司 万向机械手
US20160251781A1 (en) * 2013-10-15 2016-09-01 Oerlikon Textile Gmbh & Co. Kg Roller
US10443652B2 (en) * 2013-03-09 2019-10-15 Waukesha Bearings Corporation Countershaft

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6175767A (ja) * 1984-09-14 1986-04-18 Nobuyuki Hirohata ロ−ル

Citations (5)

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Publication number Priority date Publication date Assignee Title
US3063041A (en) * 1958-08-19 1962-11-06 Ibm High speed reaction drum
US3374039A (en) * 1965-09-01 1968-03-19 Gen Motors Corp Antifriction bearing
US3527510A (en) * 1968-12-05 1970-09-08 Gen Motors Corp Antihammer device for air spindles
US3645589A (en) * 1970-12-03 1972-02-29 Gen Motors Corp Air bearing with low tensile strength permeable sleeve
US3645590A (en) * 1970-12-17 1972-02-29 Gen Motors Corp Carbon-graphite gas-bearing roll

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3063041A (en) * 1958-08-19 1962-11-06 Ibm High speed reaction drum
US3374039A (en) * 1965-09-01 1968-03-19 Gen Motors Corp Antifriction bearing
US3527510A (en) * 1968-12-05 1970-09-08 Gen Motors Corp Antihammer device for air spindles
US3645589A (en) * 1970-12-03 1972-02-29 Gen Motors Corp Air bearing with low tensile strength permeable sleeve
US3645590A (en) * 1970-12-17 1972-02-29 Gen Motors Corp Carbon-graphite gas-bearing roll

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3994193A (en) * 1973-10-01 1976-11-30 Domtar Limited Air bearing slitter
US3986650A (en) * 1974-09-10 1976-10-19 Eastman Kodak Company Positionally constraining web support
US4098115A (en) * 1976-01-14 1978-07-04 Bayer Aktiengesellschaft Yarn tension measuring device
US4294494A (en) * 1978-12-04 1981-10-13 Hitachi, Ltd. Sliding-type bearing
US4610060A (en) * 1984-08-27 1986-09-09 Eastman Kodak Company Drafting system for yarns
US4759249A (en) * 1985-09-21 1988-07-26 Maschinenfabrik Goebel Gmbh Web slitting apparatus having adjustable lower cutting blades
US5069558A (en) * 1989-11-25 1991-12-03 Fag Kugelfischer Georg Schafer Air-supported laying roller for textile yarn
US5224641A (en) * 1990-08-23 1993-07-06 Storage Technology Corporation Air bearing for tape drive
DE4117388A1 (de) * 1991-05-28 1992-12-03 Koenig & Bauer Ag Walze zum fuehren einer warenbahn
US5246155A (en) * 1991-05-28 1993-09-21 Koenig & Bauer Aktiengesellschaft Air supported web guide roller with end seal covers
US20080148734A1 (en) * 2004-12-23 2008-06-26 Alstom Technology Ltd Power plant
CN103189659A (zh) * 2010-10-29 2013-07-03 奥依列斯工业株式会社 滚筒装置
CN103189659B (zh) * 2010-10-29 2015-11-25 奥依列斯工业株式会社 滚筒装置
WO2013098680A1 (en) * 2011-12-29 2013-07-04 Lakshmi Machine Works Ltd. An improved sliver guide arrangement in a textile machine
US10443652B2 (en) * 2013-03-09 2019-10-15 Waukesha Bearings Corporation Countershaft
US20160251781A1 (en) * 2013-10-15 2016-09-01 Oerlikon Textile Gmbh & Co. Kg Roller
US9932694B2 (en) * 2013-10-15 2018-04-03 Oerlikon Textile Gmbh & Co. Kg Roller
CN105386134A (zh) * 2015-12-04 2016-03-09 浙江古纤道新材料股份有限公司 万向机械手
CN105386134B (zh) * 2015-12-04 2017-12-19 浙江古纤道新材料股份有限公司 万向机械手

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NL7213070A (de) 1973-05-29
CH547222A (de) 1974-03-29
CA962730A (en) 1975-02-11
FR2162932A5 (de) 1973-07-20
DE2246903A1 (de) 1973-06-07

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