USRE31554E - Roll device - Google Patents

Roll device Download PDF

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Publication number
USRE31554E
USRE31554E US06/226,696 US22669681A USRE31554E US RE31554 E USRE31554 E US RE31554E US 22669681 A US22669681 A US 22669681A US RE31554 E USRE31554 E US RE31554E
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US
United States
Prior art keywords
roll
ring
spring element
resilient
centering
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
US06/226,696
Inventor
Sture Giege
Torgny C. B. Lagerqvist
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.)
Santrade Ltd
Original Assignee
Sandvik AB
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Filing date
Publication date
Application filed by Sandvik AB filed Critical Sandvik AB
Assigned to SANTRADE LTD., A CORP. OF SWITZERLAND reassignment SANTRADE LTD., A CORP. OF SWITZERLAND ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: SANDVIK AKTIEBOLAG, A CORP. OF SWEDEN
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Publication of USRE31554E publication Critical patent/USRE31554E/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B27/00—Rolls, roll alloys or roll fabrication; Lubricating, cooling or heating rolls while in use
    • B21B27/02—Shape or construction of rolls
    • B21B27/03—Sleeved rolls
    • B21B27/035—Rolls for bars, rods, rounds, tubes, wire or the like
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F16D1/08—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key
    • F16D1/09—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping due to axial loading of at least one pair of conical surfaces
    • F16D1/093—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping due to axial loading of at least one pair of conical surfaces using one or more elastic segmented conical rings forming at least one of the conical surfaces, the rings being expanded or contracted to effect clamping
    • F16D1/094—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping due to axial loading of at least one pair of conical surfaces using one or more elastic segmented conical rings forming at least one of the conical surfaces, the rings being expanded or contracted to effect clamping using one or more pairs of elastic or segmented rings with mutually mating conical surfaces, one of the mating rings being contracted and the other being expanded
    • 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
    • F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
    • F16C2226/10—Force connections, e.g. clamping
    • F16C2226/16—Force connections, e.g. clamping by wedge action, e.g. by tapered or conical parts
    • 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
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T403/00—Joints and connections
    • Y10T403/70—Interfitted members
    • Y10T403/7047—Radially interposed shim or bushing
    • Y10T403/7051—Wedging or camming
    • Y10T403/7052—Engaged by axial movement
    • Y10T403/7056—Threaded actuator

Definitions

  • This invention relates to an arrangement in a roll assembly.
  • a conical centering sleeve is forced in between a roll ring and a roll shaft whereby the torsional moment is transmitted to the roll ring by this clamping-joint.
  • the advantage of this joint is that the roll ring and roll shaft can be manufactured with great margins and that the roll ring can easily be exchanged.
  • a troublesome drawback is that, when the conical sleeve is forced in between the roll ring and roll shaft, so great tensile stresses are introduced into the roll ring, which in most cases is made of cemented carbide, that it bursts.
  • a third type of joint the roll ring is prevented to rotate relatively the roll shaft by axial clamping, whereby the axial force is kept within fixed limits by applying a spring element in connection to the roll ring.
  • the drawbacks of this joint is that it requires narrow tolerances on roll ring and roll shaft which makes the production of roll ring and roll shaft expensive and which makes it difficult to mount the roll ring onto and to dismount it from the shaft.
  • the present invention relates to a joint that eliminates the drawbacks mentioned above and which allows large torsional moments to be transmitted, and wide tolerances to be used.
  • the production costs for the roll ring and roll shaft will be relatively low.
  • the joint allows a quick exchange of roll rings, since partly the roll ring is easy to dismount, partly easy to mount.
  • FIG. 1 shows in longitudinal section one embodiment of the invention
  • FIG. 2 shows another embodiment of the invention in longitudinal section.
  • FIG. 1 there are shown two roll rings 1,2 (three or more roll rings can of course be mounted on the roll shaft) mounted on a roll shaft 3, whereby the clearances are so great that both mounting and dismounting of the roll rings can be made quickly and simply by hand.
  • the roll joint must be provided with centering elements which are in the form of two pairs of wedge-type centering sleeves 4,5 or 7 bearing against each other and mounted between the roll ring and roll shaft. Thanks to the fact that two or several wedge-type centering sleeves are used the roll shaft or the inner surface of the roll ring does not have to be conical but can be straight. Bearing against one of the centering sleeves 5 or 7 4,6 of each pair is a resilient element 8, or 9 having a small spring force.
  • a distance ring 10 Radially outside the element 8 and bearing against the roll ring 1 there is positioned a distance ring 10. Another distance ring 11 is positioned between the two roll rings 1 and 2 and has one part bearing against the upper part of the resilient element 9. Another resilient element 12 having very great spring force is positioned axially outside the resilient element 8 and the distance ring 10. The resilient element 12 has an upper part bearing against the distance ring 10 and another part bearing against an upper part of the resilient element 8. Axially outside the resilient element 12 and bearing against the same there is positioned a press ring 13 which partially surrounds a mechanical lock nut 14 acting on the press ring 13. In order to effect the axial press force on the roll joint a suitable hydraulic press element is applied against the press ring.
  • FIG. 2 there is shown another embodiment of the roll joint.
  • a roll ring 22 is mounted on a roll shaft 21 whereby a centering element in the form of a conical sleeve 23 is mounted between the ring and shaft.
  • a centering element in the form of a conical sleeve 23 is mounted between the ring and shaft.
  • part of the shaft that is in contact with the sleeve 23 is tapered in order to provide a good contact surface for the conical sleeve 23.
  • a resilient element for instance a belleville washer 24 having very great spring force.
  • another resilient element for instance a cup spring 25 having a small spring force.
  • the resilient element 25 has not the same radial extension as the resilient element 24 and is positioned axially outside the same.
  • a press ring 26 which wholly or partially surrounds a mechanical lock nut 27.
  • a hydraulic nut or a similar device is used.
  • the centering sleeve (or sleeves) can be forced in between the shaft and the ring with a fixed force which is small in relation to the axial clamping force on the roll ring and, which is transmitted from the press ring by the first resilient element at the same time as the axial clamping force from the press ring is applied on the roll ring by the second resilient element, the spring force of which is many times greater than that of the first element.
  • the mounting is made in one operation, whereby axial clamping of the roll ring for transmission of the torsional moment is obtained at the same time as the roll ring is centered and gets support at its inner diameter by the centering sleeve without undesirable and injurous tensile stresses being introduced into the roll ring.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Reduction Rolling/Reduction Stand/Operation Of Reduction Machine (AREA)
  • Rolls And Other Rotary Bodies (AREA)

Abstract

A roll device includes a roll shaft and at least one roll ring mounted on the roll shaft. A lock means is securable to the roll shaft. A centering element is disposed between the roll ring and the roll shaft to center the roll ring. A first resilient element is axially interposed between the lock means and the centering element. A second resilient element is axially interposed between the lock means and the roll ring. The lock means applies axial force to the first and second resilient elements to position the centering element relative to the roll ring and roll shaft, and clamp the roll ring to the roll shaft for common rotation therewith. The spring rates of the first resilient element can be made less than that of the second resilient element to regulate the relative amount of axial forces applied to these elements.

Description

This invention relates to an arrangement in a roll assembly.
When mounting a roll ring on a roll shaft different types of joints for transmitting the torsional moment from shaft to ring have up to now been used which joints have not been satisfactory.
In one joint a conical centering sleeve is forced in between a roll ring and a roll shaft whereby the torsional moment is transmitted to the roll ring by this clamping-joint. The advantage of this joint is that the roll ring and roll shaft can be manufactured with great margins and that the roll ring can easily be exchanged. A troublesome drawback, however, is that, when the conical sleeve is forced in between the roll ring and roll shaft, so great tensile stresses are introduced into the roll ring, which in most cases is made of cemented carbide, that it bursts.
In another type of joint the roll ring is forced onto the shaft, whereby the grip shall be so great that effective contact is secured and relative movement between ring and shaft is eliminated. A grip that is great enough for transmission of moment is difficult and expensive to arrange owing to the fact that narrow tolerances on roll ring and roll shaft are required. Other drawbacks are that it is difficult to mount the roll ring onto and to dismount it from the shaft, and that there is a risk that the brittle roll ring bursts when forcing it onto the shaft.
In a third type of joint the roll ring is prevented to rotate relatively the roll shaft by axial clamping, whereby the axial force is kept within fixed limits by applying a spring element in connection to the roll ring. The drawbacks of this joint is that it requires narrow tolerances on roll ring and roll shaft which makes the production of roll ring and roll shaft expensive and which makes it difficult to mount the roll ring onto and to dismount it from the shaft.
The present invention relates to a joint that eliminates the drawbacks mentioned above and which allows large torsional moments to be transmitted, and wide tolerances to be used. Thus, the production costs for the roll ring and roll shaft will be relatively low. Moreover, the joint allows a quick exchange of roll rings, since partly the roll ring is easy to dismount, partly easy to mount.
The invention shall be described more closely below with reference to the accompanying drawings, in which
FIG. 1 shows in longitudinal section one embodiment of the invention and
FIG. 2 shows another embodiment of the invention in longitudinal section.
Referring now to FIG. 1 there are shown two roll rings 1,2 (three or more roll rings can of course be mounted on the roll shaft) mounted on a roll shaft 3, whereby the clearances are so great that both mounting and dismounting of the roll rings can be made quickly and simply by hand. Owing to these great clearances the roll joint must be provided with centering elements which are in the form of two pairs of wedge-type centering sleeves 4,5 or 7 bearing against each other and mounted between the roll ring and roll shaft. Thanks to the fact that two or several wedge-type centering sleeves are used the roll shaft or the inner surface of the roll ring does not have to be conical but can be straight. Bearing against one of the centering sleeves 5 or 7 4,6 of each pair is a resilient element 8, or 9 having a small spring force. Radially outside the element 8 and bearing against the roll ring 1 there is positioned a distance ring 10. Another distance ring 11 is positioned between the two roll rings 1 and 2 and has one part bearing against the upper part of the resilient element 9. Another resilient element 12 having very great spring force is positioned axially outside the resilient element 8 and the distance ring 10. The resilient element 12 has an upper part bearing against the distance ring 10 and another part bearing against an upper part of the resilient element 8. Axially outside the resilient element 12 and bearing against the same there is positioned a press ring 13 which partially surrounds a mechanical lock nut 14 acting on the press ring 13. In order to effect the axial press force on the roll joint a suitable hydraulic press element is applied against the press ring. When the mechanical lock nut 14 has been tightened to full contact with the press ring 13, the outer axial force can be released, whereafter the roll joint is ready for use. In connection herewith it ought to be said that the distance between the lower parts of the two resilient elements 8 and 12 is so large that in spite of the full tightening of the lock nut 14 the parts do not touch each other. In FIG. 2 there is shown another embodiment of the roll joint. A roll ring 22 is mounted on a roll shaft 21 whereby a centering element in the form of a conical sleeve 23 is mounted between the ring and shaft. In this case that part of the shaft that is in contact with the sleeve 23 is tapered in order to provide a good contact surface for the conical sleeve 23. Outside the sleeve 23 and bearing against the roll ring 22 there is placed a resilient element, for instance a belleville washer 24 having very great spring force. Bearing against the centering sleeve 23 there is placed another resilient element, for instance a cup spring 25 having a small spring force. The resilient element 25 has not the same radial extension as the resilient element 24 and is positioned axially outside the same. Bearing against the two resilient elements there is a press ring 26, which wholly or partially surrounds a mechanical lock nut 27. In order to effect the axial press force a hydraulic nut or a similar device is used. When the mechanical lock nut 27 in a suitable way has been tightened to full contact with the press ring 26, the outer axial force can be released, whereafter the roll joint is ready for use.
When dismounting the roll ring an axial force is applied against the press ring 26 by member 28, whereby the locking nut can be released and threaded off. After that the press ring 26 and the resilient elements 24 and 25 are taken off. Now the centering sleeve 23 and the roll ring 22 can be removed in a suitable way for instance by pumping pressure oil into the gap between shaft 21 and centering sleeve 23.
The important thing in this invention is that the centering sleeve (or sleeves) can be forced in between the shaft and the ring with a fixed force which is small in relation to the axial clamping force on the roll ring and, which is transmitted from the press ring by the first resilient element at the same time as the axial clamping force from the press ring is applied on the roll ring by the second resilient element, the spring force of which is many times greater than that of the first element. By choosing resilient elements with different spring force the clamping forces on the centering sleeve and the roll ring can be regulated.
Thus, the mounting is made in one operation, whereby axial clamping of the roll ring for transmission of the torsional moment is obtained at the same time as the roll ring is centered and gets support at its inner diameter by the centering sleeve without undesirable and injurous tensile stresses being introduced into the roll ring.
The invention is of course not limited to the described embodiments but can be modified within the scope of the following claims. Thus, other resilient elements than cup springs and belleville washers can be used.

Claims (16)

We claim:
1. A roll device comprising:
a roll shaft,
at least one roll ring mounted on the roll shaft,
a lock member securable to the roll shaft,
centering means interposed radially between the roll ring and the roll shaft to radially center the roll ring,
a first resilient spring element arranged to resiliently transmit axial forces from said lock means to said centering means to radially center said roll ring,
a second resilient spring element arranged to resiliently transmit axial forces from said lock means to said roll ring to axially clamp the latter.Iadd., the axial forces transmitted to said roll ring being greater than the axial forces transmitted to said centering means.Iaddend..
2. Device according to claim 1, wherein the centering means comprises two wedge-shaped centering sleeves bearing against one another.
3. Device according to claim 1, wherein the centering means comprises a single conical sleeve.
4. Device according to claim 1, wherein the first resilient spring element comprises a cup spring having a smaller spring force than that of the second resilient spring element.
5. Device according to claim 1, wherein the second resilient spring element comprises a belleville washer having a larger spring force than that of the first resilient spring element.
6. Device according to claim 1, wherein the lock member comprises a threaded lock nut securable to the ring shaft and a press ring is axially interposed between the resilient spring elements on the one hand and the lock nut on the other hand.
7. Device according to claim 6, wherein the press ring includes first and second portions, said first portion acting on the first resilient spring element at the same time that the second portion acts on the second resilient spring element.
8. Device according to claim 1 further including a press ring disposed between the lock member and the second resilient element and bearing against only the second of the resilient spring elements.
9. Device according to claim 1, further including a second roll ring and a centering element therefor, a distance ring axially interposed between the roll rings, another first spring resilient element axially interposed between the distance ring and the last-named centering element, the distance ring including a first portion for engaging the other first resilient spring element and a second portion for engaging the second roll ring.
10. A device according to claim 1 wherein at least one of said spring elements receives and transmits at least some axial forces independently of the other spring element.
11. A device according to claim 10 wherein said at least one spring element has a larger spring force than said first spring element.
12. A device according to claim 10 wherein both of said spring elements receive and transmit axial forces independently of each other.
13. A device according to claim 8 wherein said second spring element is positioned axially outside of said first spring element and has a first portion acting on the first spring element and a second portion acting on a distance ring positioned radially outside of the first spring element.
14. A device according to claim 1 wherein said second spring element is disposed axially outside of said ring roll.
15. A device according to claim 1 wherein said second spring permits limited axial displacement of said roll ring during shaft rotation.
16. A device acording to claim 1 wherein said second spring extends radially beyond the centering means. .Iadd. 17. A roll device comprising:
a roll shaft,
at least one roll ring mounted on the roll shaft,
a lock member securable to the roll shaft,
centering means interposed radially between the roll ring and the roll shaft, and being arranged to transmit radial centering forces to said roll ring in response to being urged axially,
a first resilient spring element arranged to resiliently transmit axial forces from said lock means to said centering means to cause the latter to radially center said roll ring,
said centering means being arranged to transmit greater radial centering forces to said roll ring as the axial forces transmitted to said centering means are increased,
a second resilient spring element arranged to resiliently transmit axial forces from said lock means to said roll ring to axially clamp the latter, the axial forces transmitted to said roll ring being greater than the axial forces transmitted to said centering means,
at least one of said first and second spring elements transmitting forces to only one of said centering means and roll ring. .Iaddend.
US06/226,696 1977-03-21 1981-01-21 Roll device Expired - Lifetime USRE31554E (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE7703169A SE414277B (en) 1977-03-21 1977-03-21 DEVICE FOR ROLLS WITH ATMINSTONE A ROLLER MOUNT FITTED ON A ROLLER SHAFT
SE7703169 1977-03-21

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
US05/888,615 Reissue US4208147A (en) 1977-03-21 1978-03-21 Variably tensioned roll-to-shaft clamping means

Publications (1)

Publication Number Publication Date
USRE31554E true USRE31554E (en) 1984-04-17

Family

ID=20330776

Family Applications (1)

Application Number Title Priority Date Filing Date
US06/226,696 Expired - Lifetime USRE31554E (en) 1977-03-21 1981-01-21 Roll device

Country Status (7)

Country Link
US (1) USRE31554E (en)
JP (1) JPS6059043B2 (en)
BE (1) BE865111A (en)
DE (1) DE2811085C2 (en)
GB (1) GB1583711A (en)
IT (1) IT1093909B (en)
SE (1) SE414277B (en)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5109585A (en) * 1990-10-24 1992-05-05 Uwe Kark Roll for a roll stand having an exchangeable roll ring and a divided roll body
EP1312430A1 (en) * 2001-11-16 2003-05-21 Uwe Kark Rolling device
US20090280972A1 (en) * 2008-05-07 2009-11-12 Mitsubishi Materials Corporation Rolling roll, rolling ring, rolling mill, and rolling roll assembling method
US20130089371A1 (en) * 2010-05-04 2013-04-11 Mona Elisabet WINKVIST Pre-tensioning device between two elements mounted in spaced relation on an axle
CN109944870A (en) * 2017-12-21 2019-06-28 北京清大天达光电科技股份有限公司 A kind of idler wheel anti-loose structure

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63127704U (en) * 1987-02-13 1988-08-22
WO2003090947A1 (en) * 2002-04-24 2003-11-06 Koellges Ralf Device and method for mounting a roll ring onto a shaft of a rolling stand
SE528850C2 (en) * 2005-06-17 2007-02-27 Sandvik Intellectual Property Roller and spacer ring with power transmitting end surface
SE529022C2 (en) * 2005-06-17 2007-04-10 Sandvik Intellectual Property Roll and ring for roll comprising a spring means
JP4735580B2 (en) * 2006-09-19 2011-07-27 三菱マテリアル株式会社 Rolling roll, rolling ring, rolling mill and assembling method of rolling roll

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1065069A (en) * 1912-04-02 1913-06-17 American Wood Working Machinery Co Cutter-head.
GB317469A (en) * 1928-08-18 1931-01-02 Hugo Junkers Improvements in and relating to the mounting of machine parts on shafts in a manner suitable for the transmission of rotational forces
US2755093A (en) * 1953-01-02 1956-07-17 Oskar E Peter Clamping means
GB778676A (en) * 1953-11-20 1957-07-10 Heraeus Schott Quarzschmelze Improvements in or relating to textile guiding drums
US2816452A (en) * 1956-05-29 1957-12-17 American Pulley Co Adjustable sheaves
US2956826A (en) * 1955-03-02 1960-10-18 U S Automatic Corp Coupling unit
US3112116A (en) * 1961-05-25 1963-11-26 Hurth Masch Zahnrad Carl Combined centering and clamping arrangement
US3957381A (en) * 1974-09-14 1976-05-18 Ringfeder Gmbh Coaxial, double-cone, frictional hub-to-shaft connector

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1908942A1 (en) * 1969-02-22 1970-09-10 Morgan Contruction Co Fastening a roller ring on a shaft with the associated tool kit
DE2261369A1 (en) * 1972-12-15 1974-06-20 Roechling Burbach Gmbh Stahl CLAMPING DEVICE FOR ROLLER LEVELING MACHINES
DE2549709C2 (en) * 1975-11-06 1985-01-03 Mannesmann AG, 4000 Düsseldorf Device for clamping a cantilevered rotating body, in particular a rolling disk made of hard metal, on a drive shaft

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1065069A (en) * 1912-04-02 1913-06-17 American Wood Working Machinery Co Cutter-head.
GB317469A (en) * 1928-08-18 1931-01-02 Hugo Junkers Improvements in and relating to the mounting of machine parts on shafts in a manner suitable for the transmission of rotational forces
US2755093A (en) * 1953-01-02 1956-07-17 Oskar E Peter Clamping means
GB778676A (en) * 1953-11-20 1957-07-10 Heraeus Schott Quarzschmelze Improvements in or relating to textile guiding drums
US2956826A (en) * 1955-03-02 1960-10-18 U S Automatic Corp Coupling unit
US2816452A (en) * 1956-05-29 1957-12-17 American Pulley Co Adjustable sheaves
US3112116A (en) * 1961-05-25 1963-11-26 Hurth Masch Zahnrad Carl Combined centering and clamping arrangement
US3957381A (en) * 1974-09-14 1976-05-18 Ringfeder Gmbh Coaxial, double-cone, frictional hub-to-shaft connector

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5109585A (en) * 1990-10-24 1992-05-05 Uwe Kark Roll for a roll stand having an exchangeable roll ring and a divided roll body
EP1312430A1 (en) * 2001-11-16 2003-05-21 Uwe Kark Rolling device
WO2003041884A1 (en) * 2001-11-16 2003-05-22 Uwe Kark Rolling device
US20090280972A1 (en) * 2008-05-07 2009-11-12 Mitsubishi Materials Corporation Rolling roll, rolling ring, rolling mill, and rolling roll assembling method
US8852065B2 (en) * 2008-05-07 2014-10-07 Mitsubishi Materials Corporation Rolling roll, rolling ring, rolling mill, and rolling roll assembling method
US20130089371A1 (en) * 2010-05-04 2013-04-11 Mona Elisabet WINKVIST Pre-tensioning device between two elements mounted in spaced relation on an axle
CN109944870A (en) * 2017-12-21 2019-06-28 北京清大天达光电科技股份有限公司 A kind of idler wheel anti-loose structure
CN109944870B (en) * 2017-12-21 2023-12-29 北京清大天达光电科技股份有限公司 Anti-loosening structure for roller

Also Published As

Publication number Publication date
DE2811085C2 (en) 1986-07-31
JPS6059043B2 (en) 1985-12-23
SE7703169L (en) 1978-09-22
BE865111A (en) 1978-07-17
JPS53123362A (en) 1978-10-27
DE2811085A1 (en) 1978-09-28
IT7821429A0 (en) 1978-03-21
IT1093909B (en) 1985-07-26
GB1583711A (en) 1981-01-28
SE414277B (en) 1980-07-21

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