US3302698A - Heat exchange apparatus - Google Patents

Heat exchange apparatus Download PDF

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Publication number
US3302698A
US3302698A US418598A US41859864A US3302698A US 3302698 A US3302698 A US 3302698A US 418598 A US418598 A US 418598A US 41859864 A US41859864 A US 41859864A US 3302698 A US3302698 A US 3302698A
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US
United States
Prior art keywords
shaft
bearings
shell
seals
roll
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
Application number
US418598A
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English (en)
Inventor
Donald W Edwards
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.)
EIDP Inc
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EI Du Pont de Nemours and Co
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by EI Du Pont de Nemours and Co filed Critical EI Du Pont de Nemours and Co
Priority to US418598A priority Critical patent/US3302698A/en
Priority to NL656515032A priority patent/NL151147B/xx
Priority to GB53026/65A priority patent/GB1099000A/en
Priority to CH1731865A priority patent/CH462371A/fr
Priority to BE673872D priority patent/BE673872A/xx
Priority to DE19651660564 priority patent/DE1660564C3/de
Application granted granted Critical
Publication of US3302698A publication Critical patent/US3302698A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • D—TEXTILES; PAPER
    • D06—TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
    • D06B—TREATING TEXTILE MATERIALS USING LIQUIDS, GASES OR VAPOURS
    • D06B23/00—Component parts, details, or accessories of apparatus or machines, specially adapted for the treating of textile materials, not restricted to a particular kind of apparatus, provided for in groups D06B1/00 - D06B21/00
    • D06B23/02—Rollers
    • D06B23/028—Rollers for thermal treatment
    • D—TEXTILES; PAPER
    • D02—YARNS; MECHANICAL FINISHING OF YARNS OR ROPES; WARPING OR BEAMING
    • D02J—FINISHING OR DRESSING OF FILAMENTS, YARNS, THREADS, CORDS, ROPES OR THE LIKE
    • D02J13/00—Heating or cooling the yarn, thread, cord, rope, or the like, not specific to any one of the processes provided for in this subclass
    • D02J13/005—Heating or cooling the yarn, thread, cord, rope, or the like, not specific to any one of the processes provided for in this subclass by contact with at least one rotating roll
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S165/00—Heat exchange
    • Y10S165/135—Movable heat exchanger
    • Y10S165/139—Fully rotatable
    • Y10S165/156—Hollow cylindrical member, e.g. drum

Definitions

  • a single fiber end may either be wrapped several times in a nonoverlapping manner around the circumference of a roll or, as in multi-end operation, a plurality of fiber ends generally in warp for mmay be brought into contact partly around two or more heated rolls.
  • a heated vapor is supplied to the roll chamber at super-atmospheric pressure through an internal passage in the shaft or axle supporting the roll.
  • shaft seals must be provided across the rotary and stationary portions of the passage so as to prevent leakage.
  • the seals serve to isolate the vapor from the shaft bearing members which due to the limitations of bearing materials and lubricants cannot operate at excessively elevated temperatures.
  • a typical roll of the type contemplated herein must operate at speeds in excess of 6,000 rpm. and must be capable of maintaining a constant surface temperature up wards of 200 C. within 11 C.
  • the seals are generally single-face rotary devices in which one component or annular member is affixed to the rotary shaft and the other to the stationary housing. Both members are modified by optically fiat, smooth end faces which are perpendicuar to the shaft axis and are urged against each other by spring loading. A seal is effected when the end faces are in close contact with each other, separated only by a thin film of the medium being confined.
  • the thickness of the film separating the seal face is a function of the viscosity of the material being sealed.
  • the corresponding film thickness will be small and actual rubbing contact of the seal face members will occur accompanied by rapid wear, overheating, and subsequent leakage along the faces.
  • most vapors such as steam have a very low viscosity hence cannot establish a sufiiciently thick lubricating film between seal faces; consequently, expected service life of the seals is exceedingly short.
  • the vapor tends to leak into operating areas, thereby creating a safety hazard to operating personnel and various additional maintenance problems. Vapor leakage may also adversely affect the shaft bearings by attacking and decomposing the vital lubricants. Because of these difiiculties, vapor-heated rolls have limited use in low-pressure and/ or low-speed applications.
  • the bearing immersed in the hot vapor must of necessity be operated without lubrication; consequent ly, it wears out rapidly, especially at high roll speeds.
  • the siphon tube for all practical purposes, becomes unsupported and is subjected to spurious vibration and deflection as the roll is driven.
  • the tube may even be wrenched off at start-up if the roll is full of condensate. In any event, the impact of the condensate further aggravates the fatigue problem and hastens failure.
  • valves are affixed to the roll periphery and are actuated by a stationary cam that is attached to rigid support and located at the lowest point of the roll. As the valves move past the cam, they are momentarily opened and slugs of condensate are discharged. Obviously, the arrangement is best suited for slow speed operation; for at high speeds, centrifugal force and high frequency opening and closing causes the spring mechanisms in the valves to jam and completely fail.
  • a principal object of this invention is to provide a high speed, heated textile-treatment roll.
  • Another object is to provide a heated, textile-treatment roll capable of maintaining a uniform, constant, surface temperature under varying thermal load conditions.
  • Another object of this invention is to provide a heated, textile-treatment roll capable of operating at high speed for prolonged durations.
  • Still another object of this invention is to provide a highspeed, vapor-heated roll adapted with relatively simple, trouble-free, condensate-removal means.
  • a further object of this invention is a high-speed vaporheated roll having a mechanical seal arrangement capable of prolonged operation at high temperatures and vapor pressures.
  • Yet a further object of this invention is a vapor-heated roll having a pressure-balanced, rotary-seal arrangement which effectively isolates the hot medium from the shaft bearings and which absorbs minimum driving torque.
  • the present invention provides a novel yarn-handling apparatus comprising (1) a shaft attached to a hollow roll, over which roll, yarn is heated and advanced; (2) a tubular support housing having spaced bearings located therein which carry the shaft while in the passageway of the support housing; (3) a steam inlet extending into the support housing between the bearings and a pair of seals surrounding the shaft, each between the steam inlet and a bearing; (4) a pair of lubricant inlets extending into the support housing for delivering a lubricant under pressure to the bearings, and the aforementioned shaft having a longitudinal passage communicating with the steam inlet and discharging to the interior of the roll.
  • the interior of the hollow roll defines a frusto-conical chamber as in FIGURE 1, or coupled with an interior wall as in FIGURE 2, constitutes an annular chamber
  • condensate as it forms, is directed to a circumferential groove and through orifices communicating therewith into a housing defining a collector chamber for condensate removal.
  • a second set of seals surrounding the shaft but located exteriorly to the bearings prevents escape of lubricant while permitting withdrawal and recirculation of the spent lubricant through an exit means located between each bearing and said second set of seals.
  • the invention contemplates a condensable-vapor-heated, textile-treatment roll comprising a cylindrical shell providing an exterior surface for contact with fibers and composed internally of an expanded frustoconical chamber having a circumferential groove at the large diameter end, a plurality of condensate orifices located about the periphery of the shell, each orifice extending through the shell wall and communicating with the groove, a collector chamber external of the shell and cooperating with the orifices for receiving and carrying away condensate, an elongated supporting axle connected to the shell and rotatably journalled in spaced bearings, an internal passageway within said axle communicating with both said shell and a first inlet means located between bearings for introducing a condensable vapor into the passageway, a first set of rotary seals interposed between the first inlet means and the adjacent bearings, a second set of rotary seals located along the axle exteriorly to the bearings and in opposed relationship to the first set of seals to enclose each of said bearing
  • FIGURE 1 shows a sectional view of the roll and its supporting shaft equipped with a symmetrical rotary seal arrangement.
  • FIGURE 2 shows a sectional view of an alternative embodiment equipped with a pre-lubricated ball bearing.
  • FIGURE 3 shows a sectional view along the AA of FIGURE 2 wherein longitudinal passageways are employed for increasing the circulation rate of the coolantlubricant.
  • FIGURE 4 shows a sectional view taken along line AA of FIGURE 1 wherein a plurality of capillary-like passageways are employed.
  • roll as used herein describes a complete selfcontained assembly to be mounted to a spinning machine frame, connected to the various service lines and placed into operation in short order.
  • the roll comprises a rotatable shell 1 which is modified and supported at one end by an elongated extension that serves as an axle 2.
  • This axle 2 is preferably fabricated of stainless steel alloy and is journalled in sleeve bearings 4 and 5 that are suitably retained in a stationary housing 3.
  • the external end of axle 2 is connected to a conventional coupling (not shown) and thence to the output shaft of an electric motor (not shown) whereby it is rotatably driven at proper speed.
  • Shell 1 is cylindrical in shape externally and is composed of tempered aluminum alloy or ordinary carbon steel or other suitable material.
  • shell 1 serves as the yarn contact surface which hereinafter is referred to as surface 6.
  • shell 1 is additionally modified by a raised shoulder 7.
  • Shoulder 7 serves as a convenient stop that prevents the yarn from inadvertently slipping off the contact surface 6 and entangling around the axle 2. It also accommodates an internal circumferential groove 8 which is described in more detail later.
  • Internally shell 1 has a frusto-conical peripheral surface which slopes gradually from a small diameter at the outboard end toward a larger diameter terminating in the groove 8. The sloping surface cooperates with the centrifugal force as the roll is driven such that condensate forming thereon is urged toward and into the groove 8 as shown by reference numeral 9.
  • Set into face 14 are one or more orifices 15 (only two are shown in the figure). These orifices 15 extend through the shell 1 wall, communicate with the groove 8 and function as constricted outlets through which condensate 9 is expelled.
  • the aperture size of the individual orifices 15 is fixed to remove condensate under maximum heat transfer loads. However, the combined aperture area is sufiiciently small to prevent excessive leakage and pressure loss of the heated vapor.
  • one orifice 15 having an aperture opening approximately .020 inch in diameter is sufiicient to meet maximum operating conditions. More than one orifice, however is used to insure that the roll will function in the event that the other becomes plugged. It is also understood that in certain processes, thermal loads and condensate formation rates may be significantly different, hence a different size orifice may be required.
  • Plenum 10 is an annular projection of housing 3 and is separated from the shoulder 7 by a narrow clearance gap 11.
  • gap 11 there is preferably a labyrinth composed of modified screw threads 12 that are machined into the plenum 19 wall.
  • the lead or direction of these threads 12 corresponds with the rotational direction of the shell 1 so that when the shell 1 is rotate-d, the threads 12 act as vanes and pump air into the plenum 10.
  • the inward movement of air checks any seepage of condensate or vapor (at atmospheric pressure) that may occur through gap 11.
  • a drain 13 located at the lowest part of the plenum 19 carries away liquid accumulating therein to a remote tank (not shown).
  • drain 13 can be connected to a suction tube and the plenum I33 partly evacuated and operated at sub-atmospheric pressure.
  • saturated steam is preferred because of its ready availability and low cost. Accordingly, the steam is conveyed into the shell 1 through an internal passageway 16 within the axle 2.
  • Passageway 16 extends longitudinally to a midpoint on the axle 2 between bearings 4 and 5, at which point it terminates into ports 17 and an annular inlet 18.
  • Inlet 18 is recessed in the housing 3 and is connected by means of supply conduit 19 to a remote steam manifold (not shown).
  • Adjacent and on either side of inlet 1% are rotary seals 20 and 2. Both are commercial type, singleface mechanical seals consisting of an annular rotary member that is amt-red to the axle 2 for the rotation therewith and a stationary member which is suitably retained in the housing 3.
  • the rotary member is adapted with a spring-loaded carbon ring 39 that is urged axially against a durable metal ring 40 on the stationary member.
  • the seal assemblies reside in recesses 22 and 23 which are flooded with a pressurized coolant-lubricant.
  • the iiuid is introduced into the recesses through a branched inlet 24 which is connected to a remote resorvoir (not shown).
  • a second set or" rotary mechanical seals 25 and 26 that are identical in structure to the aforementioned seals and likewise reside in recesses 27 and 28 which are flooded with the coolant-lubricant.
  • These seals serve to confine the coolant-lubricant within the axle 2 housing.
  • Recesses 27 and 28 are connected to a branched outlet 29 which serves to carry away spent quantities of coolant-lubricant to a remote storage container (not shown).
  • any suitable liquid preferably of sufficient viscosity, resistant to degradation at elevated temperatures, miscible with the heated medium and possessing good heat transfer and lubricating properties can be used as a coolantlubricant.
  • a polyalkylene glycol synthetic oil which is sold by the Union Carbide Corporation under the trade name of Ucon, Grade 501-18170 provides satisfactory results.
  • the oil is particularly well suited for use in the present case for if overheated its products of decomposition are a gas and a water-soluble liquid.
  • This coolant-lubricant is introduced into the cavities 22 and 23 at a slightly greater pressure than the steam, it being the purpose to force the fluid to flow along the seal interfaces into the inlet 18. In doing so, the liquid cools and lubricates the rubbing surfaces. More importantly, the liquid forms a film-thick barrier that prevents stearn escapage.
  • the negligible quantity of the coolant-lubricant that seeps into inlet 18 combines with the condensate that forms thereat and passes downward within inlet onduit 19 into a trap (not shown) from which it is expelled into a branch (not shown) of drain 13.
  • Bearings 4 and 5 are ordinary sleeve-type bearings which are adapted with thrust washers 30. These washers 3t) are fixedly attached to the hearings in a suitable manner such as by threaded fasteners or snap locks and act against the housing 3 to restrain the axle 2 from longitudinal displacement.
  • the washers 30 are modified by a plurality of radial clearances or grooves 32 that allow unrestricted passage of the coolant-lubricant into the annular running clearance 33 between the bearings and the journals.
  • the size of clearance 33 that is, the gap width and the flow path length are closely controlled so as to establish a predetermined flow rate while, at the same time, being proportioned to properly carry the imposed bearing loads.
  • clearance 33 serves as a convenient means for reducing the pressure of the liquid to near atmospheric levels before entering the recesses 27 and 23.
  • clearance 33 is adjusted to reduce the coolant-lubricant pressure to about 30 p.s.i.g. in recesses 27 and 28.
  • the coolant-lubricant can be either supercooled before being introduced into the roll or the flow rate can be increased by enlargement of the clearance 33. There is, of course, a practical limit to which clearance 33 can be increased beyond which the bearings will no longer properly carry the imposed loads.
  • the flow rate can be increased across the bearings 4 and 5, without compromising on proper running fits, by alternate passages.
  • open longitudinal grooves 34 can be added along the nonload carrying portions of the bearing housing or as shown in FIGURE 4, a plurality of longitudinal capillary-like conduits 35 can be arranged about the periphery.
  • FIGURE 2 an alternate embodiment of the roll is shown for low vapor pressure service.
  • the roll is essentially the same as in FIGURE 1, except for minor modifications which have been incorporated to provide a more simplified structure.
  • Bearing 5 is replaced by a pre-lubricated sealed ball bearing 36 eliminating thrust washers 3d, and seals 21 and 26 are housed in an opposed relationship in an enlarged recess 23 which is serially connected to recess 22 by a duct 55.
  • vapor pressures may range anywhere up to p.s.i.g., thus the resulting coolantlubricant pressure is well within the range considered light-duty service for mechanical rotary shaft seals.
  • the coolant-lubricant is introduced into recess 23 at lightly greater pressure (30 p.s.i.g. greater) than the steam and circulated through duct 55 to recess 22.
  • the coolant-lubricant functions primarily to confine the steam to inlet 18 and prevents overheating of ball bearing 36.
  • the coolantlubricant Upon entering recess 22, the coolantlubricant circulates through bearing 4 into recess 27 through grooves 34. The fluid is then returned through outlet 29 to a remote storage container. Seepage past seal 25 discharges directly into plenum while seepage past seal 26 is collected in recess 37 and then carried by tube 38 into the plenum 10.
  • shell 1 contains a narrow-annular steam chamber 42.
  • the peripheral sides of the chamber 42 slope gradually toward a larger diameter and terminate into condensate groove 8.
  • the chamber 42 is connected to passageway 16 of the axle 2 by a plurality of radial distributors 41.
  • Axle 2 is rotatably journalled Within the housing 3 at the shell 1 end in a bronze sleeve bearing 4 and at the drive end in a ball bearing 36.
  • the axle 2 is sufiiciently long and suitably modified to extend into the casing of a drive motor (not shown) and functions as an armature shaft.
  • the contact surface 6 of the roll may be maintained at any temperature between 100 C. and 200 C. within 1 C.
  • the roll is driven up to 6,000 r.p.m. with no appreciable wear on the rotary seals and relatively low expenditure of torque for driving the seals.
  • the textile treatment roll is thus characterized by many advantages which heretofore have not been afforded by prior-art treatment rolls.
  • the roll has greatly extended service life and absorbs a relatively small fraction of the power input for driving. It permits a rotary seal arrangement which affords admittance of very high vapor pressures, while the pressure across the seals is maintained arbitrarily low.
  • the instant apparatus provides a simple, reliable, condensate-removal means which is composed of no moving parts and can be readily adjusted to operate over a wide range of condensate loads.
  • a yarn handling apparatus comprising a cylindrical shell over which yarn is heated and advanced, a shaft connected to the cylindrical shell and a support housing for the shaft, said shell having a closed end outboard from the shaft and an interior peripheral frusto-conical surface sloping outwardly in a gradual manner from such end and terminating in a groove recessed in the periphery of the shell and a plurality of spaced orifices communicating "with the groove and with a collector chamber external of the shell, the said shaft being rotatably journaled in spaced bearings in the support housing and having an internal passageway communicating with the interior peripheral surface of said shell, and the said support hous- 6 ing for the shaft comprising condensible vapor inlet means communicating with the internal passageway of the shaft,
  • a pair of spaced bearings located on either side of such condensible vapor inlet means, a first set of rotary sealsinterposed between the condensible vapor inlet means and the adjacent spaced bearings to enclose said con-- densible vapor inlet means, a second set of rotary seals located along the shaft exteriorly to the pair of spaced bearings and in opposed relationship to the first set of' seals to enclose each of said bearings therebetween, pres-- surized lubricant-coolant inlet means located between the bearings and the first set of rotary seals, and exit means located between the bearings and said second set of seals for removing spent lubricant-coolant.
  • a yarn handling apparatus comprising a cylindrical shell over which yarn is heated and advanced, a shaft connected to the cylindrical shell and a support housing for the shaft, said shell having a closed end outboard from the shaft and said shaft being rotatably journeled in spaced bearings in the support housing and having an internal passageway communicating with the interior peripheral surface of said shell, and the said support housing for the shaft comprising condensible vapor inlet means communicating with the internal passageway of the shaft, a pair of spaced bearings located on either side of such condensible vapor inlet means, a first set of rotary seals interposed between the condensible vapor inlet means and the adjacent spaced hearings to enclose said condensible vapor inlet means, a second set of rotary seals located along the shaft exteriorly to the pair of spaced bearings and in opposed relationship to the first set of seals to enclose each of said bearings therebetween, pressurized lubricant-coolant inlet means located between the bearings and the first set of rotary seals
  • An apparatus suitable for the handling of yarn comprising a cylindrical shell over which yarn is heated and advanced, a shaft connected to the cylindrical shell and a support housing for the shaft, said shell having a closed end outboard from the shaft and an interior peripheral frusto-conical surface sloping outwardly in a gradual manner from such end and terminating in a groove recessed in the periphery of the shell and a plurality of spaced orifices communicating with the groove and with a collector chamber external of the shell, the said shaft being rotatably journaled in spaced bearings in the support housing and having an internal passageway communicating with the interior surface of said shell and with condensable vapor inlet means located in the support housing.

Landscapes

  • Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Yarns And Mechanical Finishing Of Yarns Or Ropes (AREA)
  • Treatment Of Fiber Materials (AREA)
  • Earth Drilling (AREA)
US418598A 1964-12-16 1964-12-16 Heat exchange apparatus Expired - Lifetime US3302698A (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
US418598A US3302698A (en) 1964-12-16 1964-12-16 Heat exchange apparatus
NL656515032A NL151147B (nl) 1964-12-16 1965-11-19 Inrichting voor het verwarmen en voor het continu voortbewegen van een of meer kunstmatige draden.
GB53026/65A GB1099000A (en) 1964-12-16 1965-12-14 Yarn handling apparatus and the use thereof
CH1731865A CH462371A (fr) 1964-12-16 1965-12-15 Appareil pour le traitement thermique des fils
BE673872D BE673872A (fr) 1964-12-16 1965-12-16
DE19651660564 DE1660564C3 (de) 1964-12-16 1965-12-16 Beheizbare Galette

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US418598A US3302698A (en) 1964-12-16 1964-12-16 Heat exchange apparatus

Publications (1)

Publication Number Publication Date
US3302698A true US3302698A (en) 1967-02-07

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Family Applications (1)

Application Number Title Priority Date Filing Date
US418598A Expired - Lifetime US3302698A (en) 1964-12-16 1964-12-16 Heat exchange apparatus

Country Status (5)

Country Link
US (1) US3302698A (fr)
BE (1) BE673872A (fr)
CH (1) CH462371A (fr)
GB (1) GB1099000A (fr)
NL (1) NL151147B (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3477500A (en) * 1967-10-27 1969-11-11 Stuart B Sear Apparatus for high-speed treatment of continuously moving material
US3794118A (en) * 1970-11-21 1974-02-26 Neumuenster Masch App Heated roller and method of heating the same
US3802494A (en) * 1970-11-21 1974-04-09 Neumuenster Masch App Apparatus for stretching extensible materials
US4478247A (en) * 1981-01-26 1984-10-23 Franz Alber Fluid coupling for hollow rotary member
US4644668A (en) * 1985-08-28 1987-02-24 E. I. Du Pont De Nemours And Company Dryer roll

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US885813A (en) * 1906-04-14 1908-04-28 Baird Machine Co Drying-out barrel.
US1097074A (en) * 1913-04-02 1914-05-19 Howard D Bennett Packing.
US1939967A (en) * 1932-05-06 1933-12-19 Pittsburgh Plate Glass Co Glass rolling apparatus
US1962803A (en) * 1931-12-21 1934-06-12 Smith Corp A O Heat exchange apparatus
US2826005A (en) * 1952-07-23 1958-03-11 Pilkington Brothers Ltd Apparatus for manufacturing flat glass in ribbon form
US2873538A (en) * 1956-07-27 1959-02-17 Rotherm Engineering Company In Liquid-tight and gas-tight rotating tubular joints

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US885813A (en) * 1906-04-14 1908-04-28 Baird Machine Co Drying-out barrel.
US1097074A (en) * 1913-04-02 1914-05-19 Howard D Bennett Packing.
US1962803A (en) * 1931-12-21 1934-06-12 Smith Corp A O Heat exchange apparatus
US1939967A (en) * 1932-05-06 1933-12-19 Pittsburgh Plate Glass Co Glass rolling apparatus
US2826005A (en) * 1952-07-23 1958-03-11 Pilkington Brothers Ltd Apparatus for manufacturing flat glass in ribbon form
US2873538A (en) * 1956-07-27 1959-02-17 Rotherm Engineering Company In Liquid-tight and gas-tight rotating tubular joints

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3477500A (en) * 1967-10-27 1969-11-11 Stuart B Sear Apparatus for high-speed treatment of continuously moving material
US3794118A (en) * 1970-11-21 1974-02-26 Neumuenster Masch App Heated roller and method of heating the same
US3802494A (en) * 1970-11-21 1974-04-09 Neumuenster Masch App Apparatus for stretching extensible materials
US4478247A (en) * 1981-01-26 1984-10-23 Franz Alber Fluid coupling for hollow rotary member
US4644668A (en) * 1985-08-28 1987-02-24 E. I. Du Pont De Nemours And Company Dryer roll

Also Published As

Publication number Publication date
DE1660564B2 (de) 1975-12-04
NL6515032A (fr) 1966-06-17
GB1099000A (en) 1968-01-10
BE673872A (fr) 1966-04-15
NL151147B (nl) 1976-10-15
DE1660564A1 (de) 1970-07-16
CH462371A (fr) 1968-09-15

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