CA1311377C - Hydraulic nut arrangement - Google Patents
Hydraulic nut arrangementInfo
- Publication number
- CA1311377C CA1311377C CA000559281A CA559281A CA1311377C CA 1311377 C CA1311377 C CA 1311377C CA 000559281 A CA000559281 A CA 000559281A CA 559281 A CA559281 A CA 559281A CA 1311377 C CA1311377 C CA 1311377C
- Authority
- CA
- Canada
- Prior art keywords
- hydraulic
- piston
- cylinder component
- roll
- ring
- 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
Links
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- 239000000463 material Substances 0.000 claims description 38
- 239000004809 Teflon Substances 0.000 claims description 10
- 229920006362 Teflon® Polymers 0.000 claims description 10
- 238000007789 sealing Methods 0.000 claims description 10
- 238000002347 injection Methods 0.000 claims description 5
- 239000007924 injection Substances 0.000 claims description 5
- 238000013022 venting Methods 0.000 claims 2
- 239000004519 grease Substances 0.000 abstract description 11
- 230000000712 assembly Effects 0.000 abstract 1
- 238000000429 assembly Methods 0.000 abstract 1
- 238000010276 construction Methods 0.000 description 14
- 229910000831 Steel Inorganic materials 0.000 description 8
- 239000010959 steel Substances 0.000 description 8
- RTZKZFJDLAIYFH-UHFFFAOYSA-N Diethyl ether Chemical compound CCOCC RTZKZFJDLAIYFH-UHFFFAOYSA-N 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 229910000906 Bronze Inorganic materials 0.000 description 2
- 239000010974 bronze Substances 0.000 description 2
- KUNSUQLRTQLHQQ-UHFFFAOYSA-N copper tin Chemical compound [Cu].[Sn] KUNSUQLRTQLHQQ-UHFFFAOYSA-N 0.000 description 2
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- 229920000459 Nitrile rubber Polymers 0.000 description 1
- 102100034742 Rotatin Human genes 0.000 description 1
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- 208000027418 Wounds and injury Diseases 0.000 description 1
- 239000002253 acid Substances 0.000 description 1
- 150000007513 acids Chemical class 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 238000005336 cracking Methods 0.000 description 1
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- JNSGIVNNHKGGRU-JYRVWZFOSA-N diethoxyphosphinothioyl (2z)-2-(2-amino-1,3-thiazol-4-yl)-2-methoxyiminoacetate Chemical compound CCOP(=S)(OCC)OC(=O)C(=N/OC)\C1=CSC(N)=N1 JNSGIVNNHKGGRU-JYRVWZFOSA-N 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 230000009977 dual effect Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- ODZBBRURCPAEIQ-PIXDULNESA-N helpin Chemical compound C1[C@H](O)[C@@H](CO)O[C@H]1N1C(=O)NC(=O)C(\C=C\Br)=C1 ODZBBRURCPAEIQ-PIXDULNESA-N 0.000 description 1
- 208000014674 injury Diseases 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000000314 lubricant Substances 0.000 description 1
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Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B31/00—Rolling stand structures; Mounting, adjusting, or interchanging rolls, roll mountings, or stand frames
- B21B31/07—Adaptation of roll neck 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
- F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
- F16B31/00—Screwed connections specially modified in view of tensile load; Break-bolts
- F16B31/04—Screwed connections specially modified in view of tensile load; Break-bolts for maintaining a tensile load
- F16B31/043—Prestressed connections tensioned by means of liquid, grease, rubber, explosive charge, or the like
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B2203/00—Auxiliary arrangements, devices or methods in combination with rolling mills or rolling methods
- B21B2203/30—Quick or bayonet couplings
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B31/00—Rolling stand structures; Mounting, adjusting, or interchanging rolls, roll mountings, or stand frames
- B21B31/07—Adaptation of roll neck bearings
- B21B31/074—Oil film bearings, e.g. "Morgoil" bearings
Abstract
ABSTRACT
A hydraulic fastener is provided for mounting bearing assemblies on the end of a roll in a rolling mill stand. The fastener includes a hydraulic ring cylinder component having a front face directed toward a roll and an inner cylindrical surface adapted to fit onto a reduced diameter end section of the roll. A chamber extends about the circumference of the cylinder component and is open at the front face. A hydraulic ring piston component is slidably received in this chamber and has an inner face. A
retaining ring is threadedly mounted in the cylinder component to hold at least a substantial portion of the piston in the chamber. Passageways are provided in the cylinder component for injecting grease into the chamber and into a space formed between the inner face of the piston and an opposing face of the chamber. A split ring is secured on the end section of the roll to retain the cylinder component in place. Zero-leakage two-directional seals are arranged between the cylinder component and the piston at both radially inner and radially outer sides of the piston to prevent escape of said grease.
A hydraulic fastener is provided for mounting bearing assemblies on the end of a roll in a rolling mill stand. The fastener includes a hydraulic ring cylinder component having a front face directed toward a roll and an inner cylindrical surface adapted to fit onto a reduced diameter end section of the roll. A chamber extends about the circumference of the cylinder component and is open at the front face. A hydraulic ring piston component is slidably received in this chamber and has an inner face. A
retaining ring is threadedly mounted in the cylinder component to hold at least a substantial portion of the piston in the chamber. Passageways are provided in the cylinder component for injecting grease into the chamber and into a space formed between the inner face of the piston and an opposing face of the chamber. A split ring is secured on the end section of the roll to retain the cylinder component in place. Zero-leakage two-directional seals are arranged between the cylinder component and the piston at both radially inner and radially outer sides of the piston to prevent escape of said grease.
Description
This invention relates to forming rolls used in metal forming and in particular to the supportinq mechanism for the bearing arrangement used to rotatably mount the large, heavy rolls, commonly called back-up and work rolls.
It is well known to mount a main roll of a rolling mill in top and bottom chalks in which are mounted suitable bearings. At the outboard and inboard end of the bearings are provided collars. In one known arrangement, the outboard collar has a bearing retainer extending around its circumference, which retainer is held in place by bolts threaded into the chalks. A thrust collar bears against the axial outer face of the outboard collar. Extendin~
about the inboard collar is a seal rin~ that is mounted by bolts to the chalks.
It is also known to use plane bearin~s (usually babbit) to rotatably support the large rolls in a rolling mill. These bearings which use a large quantity of oil in order to operate can be used in conjunction with tapered roller bearin~s mounted axially outwardly from the plane bearin~. The inner bearing support is held in place hy the use of a split ring that is threaded on the outside and that is mounted in a circumferential recess formed in the roll end.
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The split ring is held in place by a complete exterior ring having internal threads and it is this exterior ring that actually bears against the side of the inner bearin~ support. The end of the roll and its exterior ring are covered by a protective cap.
This arrangement for mounting bearings on the end of the rolls has several inherent disadvantages including the fact that the threads on the rinqs can be easily damaged and there is a possibility of injury to workmen because of the known method for tightening the threaded exterior ring (this method employs a pin and cable). The known methods for mounting the bearings is time consuming and it will be appreciated that it is important to reduce the downtime for these rolling mills as much as possible in view of the cost of such mills.
The use of a device known as "a hydraulic nut"
is known in rolling mill construction, particularly in the construction of prestressed roll stands. The device can consist of ring-shaped members, namely a ; cylinder and a piston. In one known arrangement in a rolling mill, one of these members is directly connected with a tie rod by means of a clamp nut and is displaced with the ex~ansion of the tie rod under hydraulic stressin-g, the other member resting against a support.
13~1377 For example a hydraulic stressing device as shown in U.S. patent 3,588,044 issued June 2~, 1971 to E.G.
Reichrath and ~.K. ~uchheit. The device taught in this patent specification consists of a rin~ cylinder and a ring piston surrounding a tie rod. The piston is pressed downwardly by means of screw bolts and is connected directly through a divided ring with the end of the tie rod by engaging beneath a protruberance at the end of the tie rod. Fluid pressure is used to actually expand the tie rod in order to clamp the components together with a selected clamping force.
V.S. patent 4,581,911 issued April 15, 1986 to Y. Shinomoto describes a cantilever-type rolling mill having a pair of roll shafts rotatably supported in a roll housing. The rollin~ mill includes a tension member provided axially through the center of the roll shaft and havin~ the outer end thereof projecting out of the roll shaft. There is a roll compressin~ tool detachably enqageable with the projecting end of the tension member, which tool incorporates a hydraulic piston-cylinder. The tool has a nut member threadably fitted on the outer periphery of the cylinder. An extraction ring interlocks the roll unit with the tool. An oil pressure passa~e in the cylinder communicates with an ; annular groove located at the inner end of the ; piston.
13~37~
In order to mount the roll unit, this unit is mounted on the tool by the use of the extraction ring and then the unit and the tool are fitted onto the roll shaft using a jig. Clearly this known hydraulic piston-cylinder mechanism is not used to hold any bearing arrangement for the end of the roll in place.
The hydraulic piston-cylinder mechanism or nut is single acting, that is, it cannot be pressurized hydraulically in more than one direction. It is pressurized during the mounting or assembly operation only and after this operation is completed, the pressure in this hydraulic nut is removed.
Although it is believed by the applicants that the use of hydraulic nuts to mount the bearing arrangement for a roll in a rolling mill has been proposed in the past, such proposals have not met with widespread commercial success. Some of these proposals have been in practice unworkable and because of the high cost of rolling mills in general, this industry has been reluctant to accept and adopt new construction techniques for these mills, at least until a new construction has proven itself as being a definite improvement.
A drawing produced by the Timken Company shows a hydraulic nut arrangement for holding in place a ; tapered four roll T.Q.O. roller bearing mounted on the reduced end of a work roll. The hydraulic nut is formed by two ring shaped inner and outer sections.
The outer ring section has a L-shaped cross-section and it is this section that bears against a further ring member whose inner end bears against the inner bearing support.
A
- 5 - 13~1~77 Two ring-shaped seals appear to be provided between the contacting surfaces of the inner and outer ring sections that form the hydraulic nut. Another ring member is mounted on the outer end of the roll to S bear against the outer end of the inner ring section and hold the section against axially outward movement.
According to the present invention, there is provided a hydraulic fastener for mounting one end of a roll in a rolling mill stand, which Eastener includes a hydraulic ring cylinder component having a one face extending generally perpendicular to the roll axis and an inner cylindrical surface adapted to fit onto a reduced diameter end section of the roll.
A chamber extends about the circumference of this cylinder component and i8 open at the one face. A
hydraulic ring piston component is slidably received in this chamber and has an inner face. Means are provided to retain at least a substantial portion of the piston component in the chamber. There are also passageway means in the cylinder component for injecting a hydraulic material into the chamber and into a space formed between the inner face of the piston and an opposing face of the chamber. In addition there are means for retaining the combination of the cylinder component and the piston component on the end section of the roll and zero-leakage, two-directional seals arranged between the cylinder component and the piston component at both radially inner and radially outer sides of the piston.
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13~3~7 During normal use of the rolling mill, the hydraulic fastener is maintained under hydraulic pressure to hold the bearing member in place.
In a preferred embodiment, each of these seals comprises a filled Teflon seal capable of sealing off hydraulic material under pressure of at least lO,000 psi. Also, the preferred seals are two directional, that is, capable of sealing in either of two directions, for reasons which will be clear from the following description.
If desired, there can be provided a mechanical locking device capable of holding the end of the roll in place in event of failure of the hydraulic cylinder and piston components. This locking device includes a locking ring threadably mounted on the exterior of the ring cylinder.
Further features and advantages will be become apparent from the following detailed description of a preferred embodiment taken in conjunction with the accompanying drawings.
In the drawings, - Figure l is a horizontal cross-section of a back-up roll in a rolling mill, which roll i5 provided with plane bearings;
Figure 2 is a detailed view, again in cross section, of the mounting arran~ement at one end of the back up roll as shown in Figure 1, which view shows a hydraulic fastener constructed in accordance with the invention;
Figure 3 is an end view of the piston used in the hydraulic fastener of Figure 2, which view shows the end facing towards the inner bearing support;
Figure 4 is a cross-sectional view of the piston taken along the line IV-IV of Figure 3;
Figure 5 is an end view of the cylinder component used in the hydraulic fastener of Figure 2, which view sho~s the front face directed towards the roll;
15Figùre 6 is a cross-sectional view of the cylinder component, which view is taken along the line VI-VI of Figure 5 Figure 7 is another cross-sectional view of the ' cylinder component taken along the line VII-VII of Figure 5;
- Figure 8 is an outer end view of a retaining ,; ring used in the hydraulic fastener of Figure 2:
Figure 9 is an inner end view of one half of the split ring used to mount the hydraulic fastener of Figure 2;
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Figure ln is a right side view of the split ring component shown in Figure 9.
Figure 11 is an axial cross-sectional view similar to Figure 2 but illustrating an alternate version of the invention used in conjunction with four rows of roller bearings.
Figure 12 is an axial cross-sectional view of another embodiment shown in a back-up roll application, which embodiment employs a mechanical locking device in addition to the hydraulic nut.
Figure 13 is an axial cross-section of another embodiment of the hydraulic nut, which nut is capable of removing the bearing for the roll Figure 14 is an axial cross-section of another embodiment of the hydraulic nut provided with a rotatin~ seal and retaining ring located at the radially outer surface of the nut;
Figure 15 is a cross-sectional detail of a hydraulic nut illustrating the hydraulics provided to expand the nut; and Fi~ure 16 is another cross-sectional detail of the hydraulic nut of Fi~ure 15 but showing the hydraulics provided to retract the nut.
Except for the hydraulic fastener of the present invention used therein, the mountin~
arrangement for a backup roll 10 shown in Figure 1 is of standard configuration. The particular backup roll shown employs two plane bearings 12. For purposes of these bearings the roll ln has a tapered end section 14 located at each end of the roll. ~ach g end section 14 fits into a tapered bearing sleeve 16.
Each of these plane bearing sleeves is mounted in a bottom chock lR and a top chock 2n. These chocks are mounted in roll housing 22 for the operating side of the roll and roll housing 23 for the drive side of the roll.
Extending axially outward fro~ each end section 14 is a generally cylindrical, reduced diameter end section 24 and fixedly mounted on the end section 24 is an inner bearing support 26. It will be understood that the support 26 rotates with the roll ln. The inner end of the support ~6 rests against a ring collar 28. There is also an outer bearing support 3n and between the supports 26 and 3n are tapered roller bearings 32. The outer bearing lS support 30 is ~ounted in support ring 34 to which is attached a circular end plate 36 having an opening through which extends the reduced diameter end of the roll 10. Attached to the plate 36 is an end cover 38 which protects the end of the roll and the hydraulic fastener arranged thereon. The end cover 38 is detachably connected by means of bolts 40.
Although the present invention as illustrated in Figure 1 is employed in conjunction with a backup ; roll supported by plane bearings, it will be appreciated that the present invention can also be used in conjunction with rolls supported by roller bearings only. For exa~ple it is known to mount each reduced end of a roll with 4 rows of roller bearings and the hydraulic fastener of the present invention lo - 13~1~77 can be used to support the inner bearin~ support for these rows of bearin~s. Such an arrangement is shown in Figure 11 referred to hereinafter. The hydraulic fastener of the ~resent invention can be used in the mountin~ of work rolls as well as backup rolls. Also although Figure l only illustrates the present hydraulic fastener on the operator side of the roll, it is also used on the drive side of the roll.
Reference will now be made to the construction of the roll neck on which the hydraulic fastener 42 of the invention is mounted. The reduced diameter end section 24 includes an end portion 44 that is further reduced in diameter. Extendiny around the end portion 44 i5 a circumferential recess 46 which separates a head portion located at the very end of the roll from the remainder of the end portion 44.
The illustrated head portion 48 has the same diameter as the remainder of end portion 44. In the illustrated roll, a rounded shoulder 50 is formed where the end section 24 meets the end portion 44, in order to prevent stress failure or stress cracking where the diameter of the roll is reduced.
The principle components of the hydraulic fastener 42 are shown in Figure 2 in an assembled condition and these components include a hydraulic ring cylinder component 52 having a front face 54 directed towards the roll, a hydraulic ring piston component 56, and a retainer rin~ 58 for retainin~ at least a substantial portion of the piston 56 in the cylinder component 56. The component 52 has an inner cylindrical surface ~0 adapted to fit onto the reduced diameter end section or end portion 44 of the - ll 131~377 roll. A chamber 62 extends about the circu~ference of the cylinder component 52 and is open at the front face 54.
The preferred piston component 5Ç will now be described in detail with reference to Fi~ures 3 and 4 The piston has a relatively narrow outer face 64 and a wider inner face 66. The piston has a cylindrical surface 68 extendin~ about its interior and extendinq from a point near the outer face 64 to a point past the transverse center of the piston. A shoulder 7n extends radially inwardly from the surface 68 to form a wide end section 72 of the piston. Located in the radially inner side of the piston component 56 is a recess 74 of generally rectangular cross section. A
similar recess 76 is located in a radially outer side of the piston. Also in the radially outer side of the p~ston is a further recess 78 that extends to the outer face 64. The rece~s 78 includes a conical surface 8n that tapers sli~htly outwardly in the direction of the inner face 66 and a rounded surface 82 that extends to the radially outer side of the piston.
Located in the outer face 64 of the piston are four small holes 84 that are drilled and tapped. The holes 84 are used to lift the piston component 56 and mount it in the cylinder component 52. Similar holes (not shown) are also preferably provided on the axial outside surface of the cylinder component for the same reason.
A preferred type of steel for both the piston 56 and the cylinder in which it is mounted is heat treated 4340 steel. Another type of suitable steel is 5210n heat treated steel. ~ependin~ upon the application other types of material may also be used (such as high strength aluminum).
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Prefera~ly the inner corners of the ~iston at R5 and 86 are mitred at a 45 an~le as shown in Fi~ure 4.
Mounted in each of recesses 74 and 7h are zero-leakage, two-directional seals 88 and 89 which effectively seal any s~ace hetween the cylinder component and the piston. Preferably each of these seals comprises a filled Teflon* seal capable of sealin~ off the hydraulic material, i.e. grease, used to operate the hydraulic fastener. A typical minimum pressure for this grease is 2,000 psi. A
particularly preferred form of Teflon seal is bronze-filled. Each of the preferred seals 88 and ~9 includes a suitable ener~izer indicated at 9n in Fi~ure 2 which supports the filled Teflon seal and is located in back thereof. A preferred ener~izer is made from Buna-N rubber. Another suitable material is VITON (trademark) which has the advantage of being impervious to acids and water. The preferred bronze-filled Teflon seal mentioned above is available from Double Seal comPany of Fortworth, Te~as. The material used in the seal is Model No.
MNM114 or MNM118. Such seals are also available from Kaydon of Baltimore, Maryland under Model No. K3nT.
The construction of the cylinder com~onent 5~
will now be described with reference to ~igures 5 to 7.
*trade mark .
As indicated above, the component 52 has the chamber 62 extending about its circumference and open at the front face 54. The chamber 62 is sized to snuggly accommodate the above described piston component 56.
The depth of the chamber 62 is less than the depth of the piston component as can be seen from Figure 2.
However the depth of the cylinder component is greater at the radially outer side thereof, there being a projecting lip 92 that is threaded on the radially inner side thereof. The lip 92 thus forms a circular opening or recess 94 for receiving the aforementioned retaining ring 58 described further hereinafter. A small recess 96 is formed in the shoulder that extends between the edge of the chamber lS 62 and the lip 92 and this recess accommodates a static seal such as a Buna N O-ring.
The lip 92 and the radially outer side of the cylinder form a sloping surface 98 which extends along a correspondingly sloping surface formed on the in plate 36 (see Figure 2). Another shorter sloping surface 100 is formed on the rear face of the cylinder a short distance from the inner cylindrical surface 102. The sloping surface lOn provides a ; means for securing a split ring 104 in place as explained hereinafter.
Passageway ~eans are provided in the cylinder component 52 for injecting a hydraulic material, such as ~rease, into the chamber 62 and into a space formed between the inner face of the piston and the opposinq face ln6 of the chamber 62. A preferred form of passa~eway is shown in detail in Figure 6.
In particular a passageway 10~ extends fro~ the rear face of a cylinder to a radially extending passageway 110. At its inner end, the passageway 110 opens into the chamber 62 immediately adjacent to the bottom lnh thereof. The radially outer end of passageway lln opens into the radially outer surface of the cylinder. ~oth outer ends of passa~eways ln~ and lln are widened and threaded at 111 and 112 to permit the attachment of hydraulic fittings. In particular a charging fitting is attached at 111 and a pressure relief fitting is attached at 112. Also for~ed about the outer end of a passaqeway ln~ is a wide circular recess 114 into which is fitted a cylindrical guard 116 for the fitting. These guards are shown in Figure 2 of the drawings. It will be understood that in order to push the piston component out of the cylinder co~ponent 52, it is Bimply necessary to force grease through the passageway 1 n~ and the passageway 110 into the cha~ber 62.
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,i~ . , - 1; - 1311377 ~,rease is prevented from passin~ out of the opening at 112 by the fitting inserted into the openinq 112 except when the pressure exceeds a predetermined limit. A suitable ~rease for this purpose is general purpose mill ~rease. Pressures in this hydraulic nut durinq use thereof can be in excess of lO,OOn psi.
As indicated in Figure 5 there are three of the passageways llO for injecting ~rease into the cylinder to~ether with the accompanyin~ fittin~s.
Two of these are located adjacent one another on one side of the cylinder co~ponent and the third is located diametrically opposite one of the other two pas~a~eways.
Preferably there are also provided passa~eway means in the cylinder component for injecting a hydraulic material such as grease into the chamber 62 and into another space 12n, one side of which is defined by part of an outer face of the piston component 56. Injection of hydraulic material through this passageway acts to push the piston component further into the chamber. This step is used when it is desired to remove the roller bearinqs for the roll.
~311377 This further passaqeway is shown in Fiqure 7 and it includes a section 122 that is parallel to the cylindrical surface ln2 and a sloping section 124 that extends from the innermost end of the passaqeway 122 to a corner of the chamber 62. The outer end of passageway 122 is widened and threaded to accommodate a grease fitting at 126. The fitting itself is a standard charging fitting for grease and therefore has not been illustrated in the drawin~s. Aqain the ln outer end of the passa~eway 122 is provided with a relativel~ wide circular recess 128 into which is fitted a cylindrical guard for the fitting. Again there are three of the passageways 122 and 124 provided as indicated in Figure 5 of the drawings.
lS Figure 8 illustrates the retaininq ring ~8 which is used to retain at least a substantial : portion of the piston 5~ in the chamber ~2. This ring can be made from AISI 4340 steel which has been quenched and tempered and stress relieved. The rinq has threads 130 extendin~ about its circumference in order that it can be threaded into the aforementioned opening in the front face of the cylin~er.
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- 17 - 13~1377 These threads should be stron~ enough to he ahle to withstand a maximum outward hydraulic force on the piston component. A suitable thread ~or this purpose is 60 truncated V-thread. Preferably the retaining ring is locked in place and this can be done by a lockin~ screw (not shown) that extends through a hole in the cylinder component 52. Extendin~ about the circumference of the retaining rin~ and located centrally on the interior surface is a recess 1~ of generally rectan~ular cross section. Positioned in , this recess is a suitable seal 134 to prevent the hydraulic material from passin~ between the retainer rin,q and the adjacent side of the piston component 56. ~referably this seal is"~una-N O-rinq seal provided with a back-up rin~ seal.
Instead of usin~ the illustrated seal 134, the seal could be a Teflon*-filled seal constructed in the same manner as the seal 89 described above. This more expensive type of seal would be used when the hydraulic fastener is adapted to retract or remove the roller bearings and their support housin~. This more expensive seal would not be required when the hydraulic fastener is not provided with the retraction capability (an optional feature).
*trade mark ' - l~ i3~ 1377 The preferred retaining ring 58 has four holes drilled into the center of its outside surface.
These holes 136 are evenly distributed about the circumference of the ring and are used to thread the retaining ring into the cylinder component with a suitable, known tool. In one embodiment these holes are 1/4 inch deep and have a diameter of 3/16 inch.
A preferred form of split ring used to secure the hydraulic fastener on the reduced end of the roll is shown in Figures 9 and 10. Only the lefthand side of the split ring is illustrated in these figures but it will be appreciated that the righthand side of the split ring is a mirror i~a~e of the illustrated half.
The two halves are bolted together by means of standard bolts that are not shown in the drawings.
The two bolts on each side extend through bolt holes 140. The illustrated split ring half 142 is attached to the roll neck in the manner shown in Figure 2 after the hydraulic fastener has been put in place.
The half 142 is generally L-shaped in cross section with an inward extension 144 defining a cylindrical surface 146, the radius of which is substantially the same as the radius of the recess 46 forming the roll neck. Another interior cylindrical surface 148 has a radius that is substantially similar to the radius of the head portion 48 of the roll neck.
- lg 1311377 These two cylindrical surfaces 14fi and 14~ are separated by a small circumferential groove 150.
A sloping surface 152 extends between the axially inside face of the split ring and the radially outer face 154. This sloping surface 1~2 serves an important function in that, in cooperation with the hydraulic nut, it helps to secure the split rings firmly onto the roll neck. The sloping surface 152 is located opposite the aforementioned sloping surface 100 located on the rear face of the cylinder component. It will be understood that extension of the piston component from the cylinder component will cause interengagement of the sloping sùrfaces, thereby providing a further mechanism for holdinn the split ring on the roll neck.
Figure 11 illustrates an alternate construction for the hydraulic fastener of the invention. Except as described hereinafter, the construction of this ~- alternative is substantially similar to that described above. The hydraulic fastener or hydraulic nut is held in position on the reduced end of the roll by a split ring 162 similar to that shown in Figures 9 and 10. However instead of bearing -~' directly against the inner bearing support, the piston of the hydraulic fastener bears against a solid steel ring 164 that extends about the reduced end portion 166 of the roll.
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- ~n 1~1137 ~
The inner face of the rinq 164 axially supports and positions the inner bearing support 168 which rotates with the roll. It will be particularly noted that in this embodiment there are two bearing supports lh~
! 5 required to support four rows of bearin~s 17n. This configuration is an example of a bearing arranqement that can be used in place of the plane bearing arrangement shown in Fi,qure 1.
The embodiment of Fi~ure 11 is equipped with a mechanical locking device 172 capable of holdinq the , roller bearin~s in place (and therefore the end of the roll in place) in event of failure of the hydraulic fastener 160. The ring 172 has an inwardly extendin~ flan~e 174 having an inner diameter which is less than the outer diameter of an outwardly extending flange 176 formed on the rin~ ],64. After the bearinqs have been secured in place using the hydraulic fastener, the flange 174 is hrought into ~, close engagement with the flanqe 17~. It will be readily seen that in the event that the hydraulic fastener should fail, outward movement of the ring 164 is still prevented by the ring 172 and its flange 174. Leaka,qe of lubricant from the bearings 17n is prevented by a suitable seal 178 which i.s secured in place by a further rinq 18n detachably connected to the ring 172 by bolts 182.
- 21 - 131137~
The space between the hydraulic nut 16~ and the ring 164 is protected by a lip seal 1~4 of known construction. This circumferential extending seal is firmly mounted on the outside of the cylinder of the 5 hydraulic fastener 160.
Figure 12 illustrates another embodiment of the hydraulic fastener of the present invention, which fastener is provided with a mechanical lockinq device. The reduced end 190 of a back-up roll 192, only a portion of which is shown, has mounted thereon a hydraulic fastener 194. This hydraulic fastener is constructed in a similar fashion to the hydraulic fastener already described and illustrated in Figure 2 of the drawings. The hydraulic fastener is held in place by a split ring 196 which is connected to the roll neck 198. Also shown in Figure 12 is the inside , section 200 of a plane bearing, which section rotates with the roll 192. It will be understood that this inside section has a polished surface at 202. A
portion of a retaining collar 204 of known ~ construction is also shown in Figure 12.
; Unlike the hydraulic nut of Figure 2, the hydraulic nut 194 is threaded on its outer surface at 206. There is provided on this outer surface a mechanical lockin~ ring 208 that is internally threaded. Also provided in this version of the invention is a further mechanical locking ring 210.
1 3 ~ 7 It is arranged between the hydraulic nut 194 and the plane bearing 200. In the installation of the bearing 200, the locking ring 210 is placed in the position shown in Figure 12 and then the hydraulic nut 194 is expanded (by injection of grease) so that it bears firmly against the ring 210. After this operation has been carried out, the locking ring 208 can then be threaded further towards the right in Figure 12 so that it also bears firmly against the locking ring 210 as shown. It will thus be seen that in the event of failure of the hydraulic nut 194, the locking ring 210 and the plane bearing 200 will still bè held firmly in place by the mechanical locking ring 208.
In the embodiment of Figùre 13 there is a hydrualic nut 230, only portions of which are shown for ease o illustration. This hydraulic nut includes a ring cylinder component 232 and a ring piston component 234. In this version the piston component has an axial extension 236 which projects a substantial distance inwardly from the inner face 238 of the cylinder component. The extension 236 has a radially outwardly extending flange 240 which forms means for pulling an adjacent bearing member. This flange fits under a ring member 242 that is bolted to the inside section 244 of a plane bearing, which section rotates with the roll. The ring member 242 has a radially inwardly extending flange 246 whose interior diameter is less than the exterior diameter of the flange 240. It will be readily seen that retraction , of the piston component 234 into the cylinder 1311~7~
_ 23 component will also cause retraction of the inside section 244 of the bearing. In this way the hydraulic nut 230 serves the dual function of not only holAing the bearing component in place but also helpin~ to remove the bearing component when this is required.
The construction o~ the end of the roll in the embodiment of Figure 13 should also be noted. The reduced dia~eter end section 250 is provided with a shoulder at 252 against which part of the inner surface 238 of the cylinder component rests. Thus axially inward movement of the cylinder component beyond the shoulder 252 is prevented.
As in the above described version of the roll, there is a circumferential recess 254 near the outer end of the roll. A suitable split ring 25h which holds the hydraulic nut 230 in place extends into the recess 254.
There is also shown in Figure 13 part of a retaining collar 257 of known construction. A seal (not shown) is arranged between the hydraulic nut 230 and the retaining collar 257 in the gap 258.
Figure 14 is a cross-sectional detail showing another version of the hydraulic nut of the invention being used to retain the bearings of a working roll.
For ease of illustration, the hydraulic nut 260 has only been shown in outline in Fiqure 14 but it will be appreciated that the nut 2hO is similar in its construction to the hydraulic nut of Fi~ure 2 except as explained hereinafter. The nut 260 is held in - ~4 - 13~1377 place by a suitable split ring 262 that is mounted in a circumferential recess formed in the roll.
Extending about the radially outer surface of the hydraulic nut is a hydraulic nut retaining ring 2~4 which is attached by bolts 266 to the side of the chock 268. The retaining ring 264 has an axially extending flange 27n that extends inwardly between the chock 268 and the cylinder component ~72 of the hydraulic nut. In order to seal the gap between the hydraulic nut and the retaining ring 2h4 there is a rotating seal 274 which could be a lip seal or a filled Teflon* seal. The particular form of this seal would depend upon the particular application.
In this embodiment the piston component of the hydraulic nut bears a~ainst a wear rin~ and spacer 276 which in turn bears against the inner roller bearing support 278. Extending about the circumference of the spacer 276 is a spring loaded garter seal 28n of known construction. Located axially outwardly from the seal 280 is a back-up ring 282 that is also a known component of a working roll bearing arrangement.
It will be seen that the configuration of Figure 14 provides an effective seal between the chock 268 and the hydraulic nut 260 located therein.
This prevents any dirt or other foreign matter from entering into the gap between the chock and the hydraulic nut where it might cause dama~e or unnecessary wear.
' * trade mark 131~77 Turning now to Figures 15 and lfi of the drawings, these drawin~s illustrate an alternative hydraulic arrangement for a hydraulic nut constructed in accordance with the invention. In particular, Figure 15 i]lustrates the passageways provided for charging and discharging the hydraulic material in order to expand the hydraulic nut. In particular, there is provided an axially extending charging passageway 290 which is provided with a threaded seat 292 to which a hydraulic line can be attached. The passage 290 has a reduced diameter end section that intersects a radially extending passageway 294. The radially outer end of the passageway 294 is sealed by a steel ball 296 which together with a spring 298 forms a high pressure relief valve. The spring ~98 is seated in a passageway 300 of increased diameter.
The spring is held in the passageway by an end plug 302 that is threaded into the cylinder component of the nut. This plug has a central passageway or vent hole at 304.
Intersecting the passageway 290 at right angles is a smaller, radially extending passageway 306 which is sealed at its outer end by a pipe plug 308.
Intersecting the passageway 306 at right angles is a short passageway 310 which opens into a seat 312 of greater diameter. At the outer end of the seat 312 is a circular recess 314 into which is fitted a protective shield (not shown) for the hydraulic connection. It will be understood that the hydraulic material is fed through the passageway 290 and the smaller passageway 294 in order to expand the nut.
The hydraulic material can be discharged or removed through the passageway 306 and the connecting passage 3ln.
Figure 16 illustrate an alternate arrangement for the hydraulics to retract the hydraulic nut. In this embodiment there is a main axially extending passa~eway 320 which has an inner portion 822 of reduced cross-section. At the outer end of the passageway 320 is a threaded seat 324 and ~llen key slot. The portion 322 is intersected at an oblique angle by a short passageway 326 which opens into the space 120 defined in part by the piston component and the retainin~ rin~ 58. It will be understood that in order to retract the nut, the user pumps the hydraulic material through a suitable hydraulic hose (not shown) that is connected up to the outer end of the passageway 320. The hydraulic material flows through the passageway 320 and through the passageway 326 into the space 12n. Excessive pressure build up is prevented by the use of a built-in pressure relief valve that includes a steel ball 32~ that is acted on by a coil spring 330. The ball 328 rests a~ainst the outer end of a short ~assageway 332 which intersects the passageway 322. The spring is held in its passageway 334 by a suitable plug 33h that is threaded into the cylinder component. The 33fi has a vent hole to permit the outward passage of gréase when this valve opens. The pressure at which the valve releases is adjustable in a known manner by means of the plug 336.
13~1~77 For the discharge of grease from the space 12n, there is provided a radially extending ~assa~eway 340 which intersects the wide section of the passageway 320. Another shorter passaqeway 342 intersects the passageway 340 at right anqles and opens into a threaded seat 344 to which a hydraulic line can be connected. The outer end of the passa~eway 3~0 is : ~locked by a pipe plug ~46. Thus, it will be understood that when the hydraulic nut is being expanded, the grease can be forced out of the space 120 and out through passageways 340 and 342 into a hydraulic line.
If desired, one can provide means for preventinq relative rotation of certain major components with respect to their adjacent components.
For example, one can provide a notch on the front face of the hydraulic piston component 56 and a cooperating keyway on the opposing face of the adjacent bearing member to prevent relative rotation.
As such means for preventin~ relative rotation are well known, these optional features have not been illustrated in the drawings. Similarly, one could provide cooperating notches and keyways between the piston component 56 and the ring cylinder component 52 and between the cylinder component 52 and the end of the roll on which it is mounted.
- 2~ -It will be clear to those skilled in this art that various modifications and chan~es can be made to the illustrated versions of the invention without departin~ from the spirit and scope of this invention. For example, instead of usin~ standard bolts to hold the split rin~ formed by the two halves 142 in place, one could use a lar~e rubber ~-rin~
that extends about the circumference of the two halves and rests in a suitable groove form~d in the outer surface of the split rin~. Also instead of two bolts on one side of the split rin~, one could employ a suitable hinge that pivotally connects the two halves to~ether. Also one could replace the s~lit rin~ with the use of thread on the inside of the cylinder com~onent 5~ and on the reduced diameter æhaft of the roll. In this embodiment the cylinder component wo~lld be threaded onto the roll end and thereby held securely in place. All such modifications and chan~es that fall within the scope of the appended claims are intended to be part of this invention.
It is well known to mount a main roll of a rolling mill in top and bottom chalks in which are mounted suitable bearings. At the outboard and inboard end of the bearings are provided collars. In one known arrangement, the outboard collar has a bearing retainer extending around its circumference, which retainer is held in place by bolts threaded into the chalks. A thrust collar bears against the axial outer face of the outboard collar. Extendin~
about the inboard collar is a seal rin~ that is mounted by bolts to the chalks.
It is also known to use plane bearin~s (usually babbit) to rotatably support the large rolls in a rolling mill. These bearings which use a large quantity of oil in order to operate can be used in conjunction with tapered roller bearin~s mounted axially outwardly from the plane bearin~. The inner bearing support is held in place hy the use of a split ring that is threaded on the outside and that is mounted in a circumferential recess formed in the roll end.
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The split ring is held in place by a complete exterior ring having internal threads and it is this exterior ring that actually bears against the side of the inner bearin~ support. The end of the roll and its exterior ring are covered by a protective cap.
This arrangement for mounting bearings on the end of the rolls has several inherent disadvantages including the fact that the threads on the rinqs can be easily damaged and there is a possibility of injury to workmen because of the known method for tightening the threaded exterior ring (this method employs a pin and cable). The known methods for mounting the bearings is time consuming and it will be appreciated that it is important to reduce the downtime for these rolling mills as much as possible in view of the cost of such mills.
The use of a device known as "a hydraulic nut"
is known in rolling mill construction, particularly in the construction of prestressed roll stands. The device can consist of ring-shaped members, namely a ; cylinder and a piston. In one known arrangement in a rolling mill, one of these members is directly connected with a tie rod by means of a clamp nut and is displaced with the ex~ansion of the tie rod under hydraulic stressin-g, the other member resting against a support.
13~1377 For example a hydraulic stressing device as shown in U.S. patent 3,588,044 issued June 2~, 1971 to E.G.
Reichrath and ~.K. ~uchheit. The device taught in this patent specification consists of a rin~ cylinder and a ring piston surrounding a tie rod. The piston is pressed downwardly by means of screw bolts and is connected directly through a divided ring with the end of the tie rod by engaging beneath a protruberance at the end of the tie rod. Fluid pressure is used to actually expand the tie rod in order to clamp the components together with a selected clamping force.
V.S. patent 4,581,911 issued April 15, 1986 to Y. Shinomoto describes a cantilever-type rolling mill having a pair of roll shafts rotatably supported in a roll housing. The rollin~ mill includes a tension member provided axially through the center of the roll shaft and havin~ the outer end thereof projecting out of the roll shaft. There is a roll compressin~ tool detachably enqageable with the projecting end of the tension member, which tool incorporates a hydraulic piston-cylinder. The tool has a nut member threadably fitted on the outer periphery of the cylinder. An extraction ring interlocks the roll unit with the tool. An oil pressure passa~e in the cylinder communicates with an ; annular groove located at the inner end of the ; piston.
13~37~
In order to mount the roll unit, this unit is mounted on the tool by the use of the extraction ring and then the unit and the tool are fitted onto the roll shaft using a jig. Clearly this known hydraulic piston-cylinder mechanism is not used to hold any bearing arrangement for the end of the roll in place.
The hydraulic piston-cylinder mechanism or nut is single acting, that is, it cannot be pressurized hydraulically in more than one direction. It is pressurized during the mounting or assembly operation only and after this operation is completed, the pressure in this hydraulic nut is removed.
Although it is believed by the applicants that the use of hydraulic nuts to mount the bearing arrangement for a roll in a rolling mill has been proposed in the past, such proposals have not met with widespread commercial success. Some of these proposals have been in practice unworkable and because of the high cost of rolling mills in general, this industry has been reluctant to accept and adopt new construction techniques for these mills, at least until a new construction has proven itself as being a definite improvement.
A drawing produced by the Timken Company shows a hydraulic nut arrangement for holding in place a ; tapered four roll T.Q.O. roller bearing mounted on the reduced end of a work roll. The hydraulic nut is formed by two ring shaped inner and outer sections.
The outer ring section has a L-shaped cross-section and it is this section that bears against a further ring member whose inner end bears against the inner bearing support.
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- 5 - 13~1~77 Two ring-shaped seals appear to be provided between the contacting surfaces of the inner and outer ring sections that form the hydraulic nut. Another ring member is mounted on the outer end of the roll to S bear against the outer end of the inner ring section and hold the section against axially outward movement.
According to the present invention, there is provided a hydraulic fastener for mounting one end of a roll in a rolling mill stand, which Eastener includes a hydraulic ring cylinder component having a one face extending generally perpendicular to the roll axis and an inner cylindrical surface adapted to fit onto a reduced diameter end section of the roll.
A chamber extends about the circumference of this cylinder component and i8 open at the one face. A
hydraulic ring piston component is slidably received in this chamber and has an inner face. Means are provided to retain at least a substantial portion of the piston component in the chamber. There are also passageway means in the cylinder component for injecting a hydraulic material into the chamber and into a space formed between the inner face of the piston and an opposing face of the chamber. In addition there are means for retaining the combination of the cylinder component and the piston component on the end section of the roll and zero-leakage, two-directional seals arranged between the cylinder component and the piston component at both radially inner and radially outer sides of the piston.
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13~3~7 During normal use of the rolling mill, the hydraulic fastener is maintained under hydraulic pressure to hold the bearing member in place.
In a preferred embodiment, each of these seals comprises a filled Teflon seal capable of sealing off hydraulic material under pressure of at least lO,000 psi. Also, the preferred seals are two directional, that is, capable of sealing in either of two directions, for reasons which will be clear from the following description.
If desired, there can be provided a mechanical locking device capable of holding the end of the roll in place in event of failure of the hydraulic cylinder and piston components. This locking device includes a locking ring threadably mounted on the exterior of the ring cylinder.
Further features and advantages will be become apparent from the following detailed description of a preferred embodiment taken in conjunction with the accompanying drawings.
In the drawings, - Figure l is a horizontal cross-section of a back-up roll in a rolling mill, which roll i5 provided with plane bearings;
Figure 2 is a detailed view, again in cross section, of the mounting arran~ement at one end of the back up roll as shown in Figure 1, which view shows a hydraulic fastener constructed in accordance with the invention;
Figure 3 is an end view of the piston used in the hydraulic fastener of Figure 2, which view shows the end facing towards the inner bearing support;
Figure 4 is a cross-sectional view of the piston taken along the line IV-IV of Figure 3;
Figure 5 is an end view of the cylinder component used in the hydraulic fastener of Figure 2, which view sho~s the front face directed towards the roll;
15Figùre 6 is a cross-sectional view of the cylinder component, which view is taken along the line VI-VI of Figure 5 Figure 7 is another cross-sectional view of the ' cylinder component taken along the line VII-VII of Figure 5;
- Figure 8 is an outer end view of a retaining ,; ring used in the hydraulic fastener of Figure 2:
Figure 9 is an inner end view of one half of the split ring used to mount the hydraulic fastener of Figure 2;
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Figure ln is a right side view of the split ring component shown in Figure 9.
Figure 11 is an axial cross-sectional view similar to Figure 2 but illustrating an alternate version of the invention used in conjunction with four rows of roller bearings.
Figure 12 is an axial cross-sectional view of another embodiment shown in a back-up roll application, which embodiment employs a mechanical locking device in addition to the hydraulic nut.
Figure 13 is an axial cross-section of another embodiment of the hydraulic nut, which nut is capable of removing the bearing for the roll Figure 14 is an axial cross-section of another embodiment of the hydraulic nut provided with a rotatin~ seal and retaining ring located at the radially outer surface of the nut;
Figure 15 is a cross-sectional detail of a hydraulic nut illustrating the hydraulics provided to expand the nut; and Fi~ure 16 is another cross-sectional detail of the hydraulic nut of Fi~ure 15 but showing the hydraulics provided to retract the nut.
Except for the hydraulic fastener of the present invention used therein, the mountin~
arrangement for a backup roll 10 shown in Figure 1 is of standard configuration. The particular backup roll shown employs two plane bearings 12. For purposes of these bearings the roll ln has a tapered end section 14 located at each end of the roll. ~ach g end section 14 fits into a tapered bearing sleeve 16.
Each of these plane bearing sleeves is mounted in a bottom chock lR and a top chock 2n. These chocks are mounted in roll housing 22 for the operating side of the roll and roll housing 23 for the drive side of the roll.
Extending axially outward fro~ each end section 14 is a generally cylindrical, reduced diameter end section 24 and fixedly mounted on the end section 24 is an inner bearing support 26. It will be understood that the support 26 rotates with the roll ln. The inner end of the support ~6 rests against a ring collar 28. There is also an outer bearing support 3n and between the supports 26 and 3n are tapered roller bearings 32. The outer bearing lS support 30 is ~ounted in support ring 34 to which is attached a circular end plate 36 having an opening through which extends the reduced diameter end of the roll 10. Attached to the plate 36 is an end cover 38 which protects the end of the roll and the hydraulic fastener arranged thereon. The end cover 38 is detachably connected by means of bolts 40.
Although the present invention as illustrated in Figure 1 is employed in conjunction with a backup ; roll supported by plane bearings, it will be appreciated that the present invention can also be used in conjunction with rolls supported by roller bearings only. For exa~ple it is known to mount each reduced end of a roll with 4 rows of roller bearings and the hydraulic fastener of the present invention lo - 13~1~77 can be used to support the inner bearin~ support for these rows of bearin~s. Such an arrangement is shown in Figure 11 referred to hereinafter. The hydraulic fastener of the ~resent invention can be used in the mountin~ of work rolls as well as backup rolls. Also although Figure l only illustrates the present hydraulic fastener on the operator side of the roll, it is also used on the drive side of the roll.
Reference will now be made to the construction of the roll neck on which the hydraulic fastener 42 of the invention is mounted. The reduced diameter end section 24 includes an end portion 44 that is further reduced in diameter. Extendiny around the end portion 44 i5 a circumferential recess 46 which separates a head portion located at the very end of the roll from the remainder of the end portion 44.
The illustrated head portion 48 has the same diameter as the remainder of end portion 44. In the illustrated roll, a rounded shoulder 50 is formed where the end section 24 meets the end portion 44, in order to prevent stress failure or stress cracking where the diameter of the roll is reduced.
The principle components of the hydraulic fastener 42 are shown in Figure 2 in an assembled condition and these components include a hydraulic ring cylinder component 52 having a front face 54 directed towards the roll, a hydraulic ring piston component 56, and a retainer rin~ 58 for retainin~ at least a substantial portion of the piston 56 in the cylinder component 56. The component 52 has an inner cylindrical surface ~0 adapted to fit onto the reduced diameter end section or end portion 44 of the - ll 131~377 roll. A chamber 62 extends about the circu~ference of the cylinder component 52 and is open at the front face 54.
The preferred piston component 5Ç will now be described in detail with reference to Fi~ures 3 and 4 The piston has a relatively narrow outer face 64 and a wider inner face 66. The piston has a cylindrical surface 68 extendin~ about its interior and extendinq from a point near the outer face 64 to a point past the transverse center of the piston. A shoulder 7n extends radially inwardly from the surface 68 to form a wide end section 72 of the piston. Located in the radially inner side of the piston component 56 is a recess 74 of generally rectangular cross section. A
similar recess 76 is located in a radially outer side of the piston. Also in the radially outer side of the p~ston is a further recess 78 that extends to the outer face 64. The rece~s 78 includes a conical surface 8n that tapers sli~htly outwardly in the direction of the inner face 66 and a rounded surface 82 that extends to the radially outer side of the piston.
Located in the outer face 64 of the piston are four small holes 84 that are drilled and tapped. The holes 84 are used to lift the piston component 56 and mount it in the cylinder component 52. Similar holes (not shown) are also preferably provided on the axial outside surface of the cylinder component for the same reason.
A preferred type of steel for both the piston 56 and the cylinder in which it is mounted is heat treated 4340 steel. Another type of suitable steel is 5210n heat treated steel. ~ependin~ upon the application other types of material may also be used (such as high strength aluminum).
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Prefera~ly the inner corners of the ~iston at R5 and 86 are mitred at a 45 an~le as shown in Fi~ure 4.
Mounted in each of recesses 74 and 7h are zero-leakage, two-directional seals 88 and 89 which effectively seal any s~ace hetween the cylinder component and the piston. Preferably each of these seals comprises a filled Teflon* seal capable of sealin~ off the hydraulic material, i.e. grease, used to operate the hydraulic fastener. A typical minimum pressure for this grease is 2,000 psi. A
particularly preferred form of Teflon seal is bronze-filled. Each of the preferred seals 88 and ~9 includes a suitable ener~izer indicated at 9n in Fi~ure 2 which supports the filled Teflon seal and is located in back thereof. A preferred ener~izer is made from Buna-N rubber. Another suitable material is VITON (trademark) which has the advantage of being impervious to acids and water. The preferred bronze-filled Teflon seal mentioned above is available from Double Seal comPany of Fortworth, Te~as. The material used in the seal is Model No.
MNM114 or MNM118. Such seals are also available from Kaydon of Baltimore, Maryland under Model No. K3nT.
The construction of the cylinder com~onent 5~
will now be described with reference to ~igures 5 to 7.
*trade mark .
As indicated above, the component 52 has the chamber 62 extending about its circumference and open at the front face 54. The chamber 62 is sized to snuggly accommodate the above described piston component 56.
The depth of the chamber 62 is less than the depth of the piston component as can be seen from Figure 2.
However the depth of the cylinder component is greater at the radially outer side thereof, there being a projecting lip 92 that is threaded on the radially inner side thereof. The lip 92 thus forms a circular opening or recess 94 for receiving the aforementioned retaining ring 58 described further hereinafter. A small recess 96 is formed in the shoulder that extends between the edge of the chamber lS 62 and the lip 92 and this recess accommodates a static seal such as a Buna N O-ring.
The lip 92 and the radially outer side of the cylinder form a sloping surface 98 which extends along a correspondingly sloping surface formed on the in plate 36 (see Figure 2). Another shorter sloping surface 100 is formed on the rear face of the cylinder a short distance from the inner cylindrical surface 102. The sloping surface lOn provides a ; means for securing a split ring 104 in place as explained hereinafter.
Passageway ~eans are provided in the cylinder component 52 for injecting a hydraulic material, such as ~rease, into the chamber 62 and into a space formed between the inner face of the piston and the opposinq face ln6 of the chamber 62. A preferred form of passa~eway is shown in detail in Figure 6.
In particular a passageway 10~ extends fro~ the rear face of a cylinder to a radially extending passageway 110. At its inner end, the passageway 110 opens into the chamber 62 immediately adjacent to the bottom lnh thereof. The radially outer end of passageway lln opens into the radially outer surface of the cylinder. ~oth outer ends of passa~eways ln~ and lln are widened and threaded at 111 and 112 to permit the attachment of hydraulic fittings. In particular a charging fitting is attached at 111 and a pressure relief fitting is attached at 112. Also for~ed about the outer end of a passaqeway ln~ is a wide circular recess 114 into which is fitted a cylindrical guard 116 for the fitting. These guards are shown in Figure 2 of the drawings. It will be understood that in order to push the piston component out of the cylinder co~ponent 52, it is Bimply necessary to force grease through the passageway 1 n~ and the passageway 110 into the cha~ber 62.
:
,i~ . , - 1; - 1311377 ~,rease is prevented from passin~ out of the opening at 112 by the fitting inserted into the openinq 112 except when the pressure exceeds a predetermined limit. A suitable ~rease for this purpose is general purpose mill ~rease. Pressures in this hydraulic nut durinq use thereof can be in excess of lO,OOn psi.
As indicated in Figure 5 there are three of the passageways llO for injecting ~rease into the cylinder to~ether with the accompanyin~ fittin~s.
Two of these are located adjacent one another on one side of the cylinder co~ponent and the third is located diametrically opposite one of the other two pas~a~eways.
Preferably there are also provided passa~eway means in the cylinder component for injecting a hydraulic material such as grease into the chamber 62 and into another space 12n, one side of which is defined by part of an outer face of the piston component 56. Injection of hydraulic material through this passageway acts to push the piston component further into the chamber. This step is used when it is desired to remove the roller bearinqs for the roll.
~311377 This further passaqeway is shown in Fiqure 7 and it includes a section 122 that is parallel to the cylindrical surface ln2 and a sloping section 124 that extends from the innermost end of the passaqeway 122 to a corner of the chamber 62. The outer end of passageway 122 is widened and threaded to accommodate a grease fitting at 126. The fitting itself is a standard charging fitting for grease and therefore has not been illustrated in the drawin~s. Aqain the ln outer end of the passa~eway 122 is provided with a relativel~ wide circular recess 128 into which is fitted a cylindrical guard for the fitting. Again there are three of the passageways 122 and 124 provided as indicated in Figure 5 of the drawings.
lS Figure 8 illustrates the retaininq ring ~8 which is used to retain at least a substantial : portion of the piston 5~ in the chamber ~2. This ring can be made from AISI 4340 steel which has been quenched and tempered and stress relieved. The rinq has threads 130 extendin~ about its circumference in order that it can be threaded into the aforementioned opening in the front face of the cylin~er.
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- 17 - 13~1377 These threads should be stron~ enough to he ahle to withstand a maximum outward hydraulic force on the piston component. A suitable thread ~or this purpose is 60 truncated V-thread. Preferably the retaining ring is locked in place and this can be done by a lockin~ screw (not shown) that extends through a hole in the cylinder component 52. Extendin~ about the circumference of the retaining rin~ and located centrally on the interior surface is a recess 1~ of generally rectan~ular cross section. Positioned in , this recess is a suitable seal 134 to prevent the hydraulic material from passin~ between the retainer rin,q and the adjacent side of the piston component 56. ~referably this seal is"~una-N O-rinq seal provided with a back-up rin~ seal.
Instead of usin~ the illustrated seal 134, the seal could be a Teflon*-filled seal constructed in the same manner as the seal 89 described above. This more expensive type of seal would be used when the hydraulic fastener is adapted to retract or remove the roller bearings and their support housin~. This more expensive seal would not be required when the hydraulic fastener is not provided with the retraction capability (an optional feature).
*trade mark ' - l~ i3~ 1377 The preferred retaining ring 58 has four holes drilled into the center of its outside surface.
These holes 136 are evenly distributed about the circumference of the ring and are used to thread the retaining ring into the cylinder component with a suitable, known tool. In one embodiment these holes are 1/4 inch deep and have a diameter of 3/16 inch.
A preferred form of split ring used to secure the hydraulic fastener on the reduced end of the roll is shown in Figures 9 and 10. Only the lefthand side of the split ring is illustrated in these figures but it will be appreciated that the righthand side of the split ring is a mirror i~a~e of the illustrated half.
The two halves are bolted together by means of standard bolts that are not shown in the drawings.
The two bolts on each side extend through bolt holes 140. The illustrated split ring half 142 is attached to the roll neck in the manner shown in Figure 2 after the hydraulic fastener has been put in place.
The half 142 is generally L-shaped in cross section with an inward extension 144 defining a cylindrical surface 146, the radius of which is substantially the same as the radius of the recess 46 forming the roll neck. Another interior cylindrical surface 148 has a radius that is substantially similar to the radius of the head portion 48 of the roll neck.
- lg 1311377 These two cylindrical surfaces 14fi and 14~ are separated by a small circumferential groove 150.
A sloping surface 152 extends between the axially inside face of the split ring and the radially outer face 154. This sloping surface 1~2 serves an important function in that, in cooperation with the hydraulic nut, it helps to secure the split rings firmly onto the roll neck. The sloping surface 152 is located opposite the aforementioned sloping surface 100 located on the rear face of the cylinder component. It will be understood that extension of the piston component from the cylinder component will cause interengagement of the sloping sùrfaces, thereby providing a further mechanism for holdinn the split ring on the roll neck.
Figure 11 illustrates an alternate construction for the hydraulic fastener of the invention. Except as described hereinafter, the construction of this ~- alternative is substantially similar to that described above. The hydraulic fastener or hydraulic nut is held in position on the reduced end of the roll by a split ring 162 similar to that shown in Figures 9 and 10. However instead of bearing -~' directly against the inner bearing support, the piston of the hydraulic fastener bears against a solid steel ring 164 that extends about the reduced end portion 166 of the roll.
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- ~n 1~1137 ~
The inner face of the rinq 164 axially supports and positions the inner bearing support 168 which rotates with the roll. It will be particularly noted that in this embodiment there are two bearing supports lh~
! 5 required to support four rows of bearin~s 17n. This configuration is an example of a bearing arranqement that can be used in place of the plane bearing arrangement shown in Fi,qure 1.
The embodiment of Fi~ure 11 is equipped with a mechanical locking device 172 capable of holdinq the , roller bearin~s in place (and therefore the end of the roll in place) in event of failure of the hydraulic fastener 160. The ring 172 has an inwardly extendin~ flan~e 174 having an inner diameter which is less than the outer diameter of an outwardly extending flange 176 formed on the rin~ ],64. After the bearinqs have been secured in place using the hydraulic fastener, the flange 174 is hrought into ~, close engagement with the flanqe 17~. It will be readily seen that in the event that the hydraulic fastener should fail, outward movement of the ring 164 is still prevented by the ring 172 and its flange 174. Leaka,qe of lubricant from the bearings 17n is prevented by a suitable seal 178 which i.s secured in place by a further rinq 18n detachably connected to the ring 172 by bolts 182.
- 21 - 131137~
The space between the hydraulic nut 16~ and the ring 164 is protected by a lip seal 1~4 of known construction. This circumferential extending seal is firmly mounted on the outside of the cylinder of the 5 hydraulic fastener 160.
Figure 12 illustrates another embodiment of the hydraulic fastener of the present invention, which fastener is provided with a mechanical lockinq device. The reduced end 190 of a back-up roll 192, only a portion of which is shown, has mounted thereon a hydraulic fastener 194. This hydraulic fastener is constructed in a similar fashion to the hydraulic fastener already described and illustrated in Figure 2 of the drawings. The hydraulic fastener is held in place by a split ring 196 which is connected to the roll neck 198. Also shown in Figure 12 is the inside , section 200 of a plane bearing, which section rotates with the roll 192. It will be understood that this inside section has a polished surface at 202. A
portion of a retaining collar 204 of known ~ construction is also shown in Figure 12.
; Unlike the hydraulic nut of Figure 2, the hydraulic nut 194 is threaded on its outer surface at 206. There is provided on this outer surface a mechanical lockin~ ring 208 that is internally threaded. Also provided in this version of the invention is a further mechanical locking ring 210.
1 3 ~ 7 It is arranged between the hydraulic nut 194 and the plane bearing 200. In the installation of the bearing 200, the locking ring 210 is placed in the position shown in Figure 12 and then the hydraulic nut 194 is expanded (by injection of grease) so that it bears firmly against the ring 210. After this operation has been carried out, the locking ring 208 can then be threaded further towards the right in Figure 12 so that it also bears firmly against the locking ring 210 as shown. It will thus be seen that in the event of failure of the hydraulic nut 194, the locking ring 210 and the plane bearing 200 will still bè held firmly in place by the mechanical locking ring 208.
In the embodiment of Figùre 13 there is a hydrualic nut 230, only portions of which are shown for ease o illustration. This hydraulic nut includes a ring cylinder component 232 and a ring piston component 234. In this version the piston component has an axial extension 236 which projects a substantial distance inwardly from the inner face 238 of the cylinder component. The extension 236 has a radially outwardly extending flange 240 which forms means for pulling an adjacent bearing member. This flange fits under a ring member 242 that is bolted to the inside section 244 of a plane bearing, which section rotates with the roll. The ring member 242 has a radially inwardly extending flange 246 whose interior diameter is less than the exterior diameter of the flange 240. It will be readily seen that retraction , of the piston component 234 into the cylinder 1311~7~
_ 23 component will also cause retraction of the inside section 244 of the bearing. In this way the hydraulic nut 230 serves the dual function of not only holAing the bearing component in place but also helpin~ to remove the bearing component when this is required.
The construction o~ the end of the roll in the embodiment of Figure 13 should also be noted. The reduced dia~eter end section 250 is provided with a shoulder at 252 against which part of the inner surface 238 of the cylinder component rests. Thus axially inward movement of the cylinder component beyond the shoulder 252 is prevented.
As in the above described version of the roll, there is a circumferential recess 254 near the outer end of the roll. A suitable split ring 25h which holds the hydraulic nut 230 in place extends into the recess 254.
There is also shown in Figure 13 part of a retaining collar 257 of known construction. A seal (not shown) is arranged between the hydraulic nut 230 and the retaining collar 257 in the gap 258.
Figure 14 is a cross-sectional detail showing another version of the hydraulic nut of the invention being used to retain the bearings of a working roll.
For ease of illustration, the hydraulic nut 260 has only been shown in outline in Fiqure 14 but it will be appreciated that the nut 2hO is similar in its construction to the hydraulic nut of Fi~ure 2 except as explained hereinafter. The nut 260 is held in - ~4 - 13~1377 place by a suitable split ring 262 that is mounted in a circumferential recess formed in the roll.
Extending about the radially outer surface of the hydraulic nut is a hydraulic nut retaining ring 2~4 which is attached by bolts 266 to the side of the chock 268. The retaining ring 264 has an axially extending flange 27n that extends inwardly between the chock 268 and the cylinder component ~72 of the hydraulic nut. In order to seal the gap between the hydraulic nut and the retaining ring 2h4 there is a rotating seal 274 which could be a lip seal or a filled Teflon* seal. The particular form of this seal would depend upon the particular application.
In this embodiment the piston component of the hydraulic nut bears a~ainst a wear rin~ and spacer 276 which in turn bears against the inner roller bearing support 278. Extending about the circumference of the spacer 276 is a spring loaded garter seal 28n of known construction. Located axially outwardly from the seal 280 is a back-up ring 282 that is also a known component of a working roll bearing arrangement.
It will be seen that the configuration of Figure 14 provides an effective seal between the chock 268 and the hydraulic nut 260 located therein.
This prevents any dirt or other foreign matter from entering into the gap between the chock and the hydraulic nut where it might cause dama~e or unnecessary wear.
' * trade mark 131~77 Turning now to Figures 15 and lfi of the drawings, these drawin~s illustrate an alternative hydraulic arrangement for a hydraulic nut constructed in accordance with the invention. In particular, Figure 15 i]lustrates the passageways provided for charging and discharging the hydraulic material in order to expand the hydraulic nut. In particular, there is provided an axially extending charging passageway 290 which is provided with a threaded seat 292 to which a hydraulic line can be attached. The passage 290 has a reduced diameter end section that intersects a radially extending passageway 294. The radially outer end of the passageway 294 is sealed by a steel ball 296 which together with a spring 298 forms a high pressure relief valve. The spring ~98 is seated in a passageway 300 of increased diameter.
The spring is held in the passageway by an end plug 302 that is threaded into the cylinder component of the nut. This plug has a central passageway or vent hole at 304.
Intersecting the passageway 290 at right angles is a smaller, radially extending passageway 306 which is sealed at its outer end by a pipe plug 308.
Intersecting the passageway 306 at right angles is a short passageway 310 which opens into a seat 312 of greater diameter. At the outer end of the seat 312 is a circular recess 314 into which is fitted a protective shield (not shown) for the hydraulic connection. It will be understood that the hydraulic material is fed through the passageway 290 and the smaller passageway 294 in order to expand the nut.
The hydraulic material can be discharged or removed through the passageway 306 and the connecting passage 3ln.
Figure 16 illustrate an alternate arrangement for the hydraulics to retract the hydraulic nut. In this embodiment there is a main axially extending passa~eway 320 which has an inner portion 822 of reduced cross-section. At the outer end of the passageway 320 is a threaded seat 324 and ~llen key slot. The portion 322 is intersected at an oblique angle by a short passageway 326 which opens into the space 120 defined in part by the piston component and the retainin~ rin~ 58. It will be understood that in order to retract the nut, the user pumps the hydraulic material through a suitable hydraulic hose (not shown) that is connected up to the outer end of the passageway 320. The hydraulic material flows through the passageway 320 and through the passageway 326 into the space 12n. Excessive pressure build up is prevented by the use of a built-in pressure relief valve that includes a steel ball 32~ that is acted on by a coil spring 330. The ball 328 rests a~ainst the outer end of a short ~assageway 332 which intersects the passageway 322. The spring is held in its passageway 334 by a suitable plug 33h that is threaded into the cylinder component. The 33fi has a vent hole to permit the outward passage of gréase when this valve opens. The pressure at which the valve releases is adjustable in a known manner by means of the plug 336.
13~1~77 For the discharge of grease from the space 12n, there is provided a radially extending ~assa~eway 340 which intersects the wide section of the passageway 320. Another shorter passaqeway 342 intersects the passageway 340 at right anqles and opens into a threaded seat 344 to which a hydraulic line can be connected. The outer end of the passa~eway 3~0 is : ~locked by a pipe plug ~46. Thus, it will be understood that when the hydraulic nut is being expanded, the grease can be forced out of the space 120 and out through passageways 340 and 342 into a hydraulic line.
If desired, one can provide means for preventinq relative rotation of certain major components with respect to their adjacent components.
For example, one can provide a notch on the front face of the hydraulic piston component 56 and a cooperating keyway on the opposing face of the adjacent bearing member to prevent relative rotation.
As such means for preventin~ relative rotation are well known, these optional features have not been illustrated in the drawings. Similarly, one could provide cooperating notches and keyways between the piston component 56 and the ring cylinder component 52 and between the cylinder component 52 and the end of the roll on which it is mounted.
- 2~ -It will be clear to those skilled in this art that various modifications and chan~es can be made to the illustrated versions of the invention without departin~ from the spirit and scope of this invention. For example, instead of usin~ standard bolts to hold the split rin~ formed by the two halves 142 in place, one could use a lar~e rubber ~-rin~
that extends about the circumference of the two halves and rests in a suitable groove form~d in the outer surface of the split rin~. Also instead of two bolts on one side of the split rin~, one could employ a suitable hinge that pivotally connects the two halves to~ether. Also one could replace the s~lit rin~ with the use of thread on the inside of the cylinder com~onent 5~ and on the reduced diameter æhaft of the roll. In this embodiment the cylinder component wo~lld be threaded onto the roll end and thereby held securely in place. All such modifications and chan~es that fall within the scope of the appended claims are intended to be part of this invention.
Claims (34)
1. A hydraulic fastener for mounting one end of a roll in a rolling mill stand comprising a hydraulic ring cylinder component having a one face extending generally perpendicular to the roll axis and an inner cylindrical surface adapted to fit onto a reduced diameter end section of said roll, a chamber extending about the circumference of and located in said cylinder component and open at said one face, a hydraulic ring piston component slidably received in said chamber and having an inner face, means for retaining at least a substantial portion of said piston component in said chamber, passageway means in said cylinder component for injecting a hydraulic material into said chamber and into a space formed between said inner face of said piston and an opposing face of said chamber, means for retaining the combination of said cylinder component and said piston component on said end section of said roll, and zero-leakage two-directional seals arranged between said cylinder component and said piston component at both radially inner and radially outer sides of said piston.
2. A hydraulic fastener according to claim l wherein each seal is capable of sealing off hydraulic material under pressure of at least 2000 psi.
3. A hydraulic fastener according to claim 1 including a mechanical locking device capable of holding said one end of said roll in place in event of failure of the hydraulic cylinder and piston components, said locking device including a locking ring threadably mounted on the exterior of said ring cylinder.
4. A hydraulic fastener according to claim 1, 2, or 3 including further passageway means in said cylinder component for injecting a hydraulic material into said chamber and into another space, one side of which is at least part of an outer face of said piston component, wherein injection of said hydraulic material through said further passageway acts to push said piston component further into said chamber.
5. A hydraulic fastener according to claim 1, 2, or 3 wherein said piston retaining means includes a retaining ring threaded into an opening in said one face of said cylinder component.
6. A hydraulic fastener according to claim 1, 2 or 3 wherein said piston retaining means includes a retaining ring threaded into an opening in said front face of said cylinder component and another zero-leakage seal is arranged between said retaining ring and one side of said piston.
7. A hydraulic fastener according to claim 1, 2 or 3 wherein said cylinder component retaining means includes a split ring detachably connectable to a neck of said roll and adapted to engage a rear face of said cylinder component.
8. A hydraulic fastener according to claim 1, 2 or 3 wherein said cylinder component retaining means includes a split ring detachably connectable to a neck of said roll and adapted to engage a rear face of said cylinder component and wherein both said rear face of said cylinder component and an axially inner face of said split ring are provided with sloping surfaces located opposite one another in the axial direction of the roll, whereby extension of said piston component from said cylinder component causes interengagement of said sloping surfaces, thereby holding said split ring on said neck.
9. A hydraulic fastener according to claim 2 wherein the seals are filled Teflon seals.
10. A hydraulic fastener according to claim 9 wherein each seal includes a suitable energizer supporting and in back of said filled Teflon seal.
11. A hydraulic fastener for mounting one end of a roll in a rolling mill stand comprising a hydraulic ring cylinder component having a front face directed towards said roll and an inner cylindrical surface adapted to fit onto a reduced diameter end section of said roll, a chamber extending about the circumference of and located in said cylinder component and open at said front face, a hydraulic ring piston component slidably received in said chamber and having an inner face, means for retaining at least a substantial portion of said piston in said chamber, passageway means in said cylinder component for injecting a hydraulic material into said chamber and into a space formed between said inner face of said piston and an opposing face of said chamber, and seals arranged between said cylinder component and said piston at both radially inner and radially outer sides of said piston, wherein said ring piston has an axial extension projecting axially outwardly from said front face of said cylinder component, said extension having means for pulling an adjacent bearing member, provided to rotatably mount said roll, when said ring piston is retracted into said cylinder component.
12. A hydraulic fastener according to claim 11 wherein said means for pulling on said bearing member comprises a radially outwardly extending flange integrally formed on said extension.
13. A hydraulic fastener according to claim 11 wherein said ring piston is recessed on one side thereof to form a second space that is closed at one end by said retaining means and closed at the opposite end by a shoulder formed on said one side of said ring piston, said fastener including further passageway means in said cylinder component for injecting a hydraulic material into said second space in order to retract said ring piston.
14. A hydraulic fastener according to claim 11, 12 or 13 including means for retaining said cylinder component on said end section of said roll.
15. A hydraulic fastener according to claim 11, 12 or 13 wherein said seals are zero-leakage, two directional seals capable of sealing off hydraulic material under pressure of at least 2000 psi.
16. A hydraulic fastener according to claim 11, 12 or 13 including a mechanical locking device capable of holding said one end of said roll in place in event of failure of the hydraulic cylinder component and the piston, said locking device including a locking ring threadably mounted on the exterior of said ring cylinder component.
17. A hydraulic fastener according to claim 11, 12 or 13 wherein said piston retaining means includes a retaining ring threaded into an opening in said front face of said cylinder component.
18. A hydraulic fastener according to claim 11, 12 or 13 wherein said seals are zero-leakage, two directional seals capable of sealing off hydraulic material under pressure of at least 2000 psi, said piston retaining means includes a retaining ring threaded into an opening in said front face of said cylinder component, and another zero-leakage, two-directional seal is arranged between said retaining ring and one side of said piston.
19. A hydraulic fastener for mounting a bearing member for one end of a roll in a rolling mill stand comprising a hydraulic ring cylinder component having one face extending perpendicular to the roll axis and an inner cylindrical surface adapted to fit onto an end section of said roll, a chamber extending about the circumference of and located in said cylinder component and open at said one face, a hydraulic ring piston component slidably received in said chamber and having an inner face, passageway means in said cylinder component for injecting a hydraulic material into said chamber and into a space formed between said inner face of said piston and an opposing face of said chamber, means for retaining the combination of said cylinder component and said piston component on said end section of said roll, and zero-leakage two-directional seals arranged between said cylinder component and said piston at both radially inner and radially outer sides of said piston.
20. A hydraulic fastener according to claim 19 including a retaining ring extending about the radially outer periphery of said cylinder component and adapted for connection to an adjacent roll chock and a rotating seal mounted between said cylinder component and said retaining ring.
21. A hydraulic fastener according to claim 19 wherein said ring piston has an axial extension projecting axially outwardly from said one face of said cylinder component, said extension having means for pulling an adjacent bearing member, provided to rotatably mount said roll, when said ring piston is retracted into said cylinder component.
22. A hydraulic fastener according to claim 21 wherein said means for pulling on said bearing member comprises a radially outwardly extending flange integrally formed on said extension.
23. A hydraulic fastener according to claim 21 wherein said ring piston is recessed on one side thereof to form a second space that is closed at one end by said retaining means and closed at the opposite end by a shoulder formed on said one side of said ring piston, said fastener including further passageway means in said cylinder component for injecting a hydraulic material into said second space in order to retract said ring piston, wherein said seals are two-directional seals.
24. A hydraulic fastener according to claim 19, 20 or 21 including a high pressure relief valve mounted in or on said cylinder component for venting hydraulic material from said passageway means when the hydraulic pressure in said space exceeds a desired upper limit.
25. A hydraulic fastener according to claim 23 including a high pressure relief valve mounted in or on said cylinder component for venting hydraulic material from said further passageway means when the hydraulic pressure in said second space exceeds a desired upper limit.
26. A hydraulic fastener according to claim 19 wherein each of said seals is a Teflon seal.
27. A hydraulic fastener according to claim 26 including further passageway means in said cylinder component for injecting a hydraulic material into said chamber and into another space, one side of which is at least part of an outer face of said piston component, injection of said hydraulic material through said further passageway acting to push said piston component further into said chamber.
28. A hydraulic fastener according to claim 2 wherein each seal is capable of sealing off hydraulic material under pressure of at least 10,000 psi.
29. A hydraulic fastener according to claim 10 wherein each seal is capable of sealing off hydraulic material under pressure of at least 10,000 psi.
30. A hydraulic fastener according to claim 11 wherein said seals are zero-leakage seals capable of sealing off hydraulic material under pressure of at least 10,000 psi.
31. A hydraulic fastener according to claim 23 wherein each seal is capable of sealing off hydraulic material under pressure of at least 10,000 psi.
32. In a rolling mill stand having a roll, a bearing member for rotatably mounting one end of said roll and a hydraulic fastener for holding said bearing member in place comprising a hydraulic ring cylinder component having one face extending generally perpendicular to the roll axis and an inner cylindrical surface adapted to fit onto a reduced diameter end section of said roll, a chamber extending about the circumference of and located in said cylinder component and open at said one face, a hydraulic ring piston component slidably received in said chamber and having an inner face, means for retaining at least a substantial portion of said piston component in said chamber, passageway means in said cylinder component for injecting a hydraulic material into said chamber and into a space formed between said inner face of said piston component and an opposing face of said chamber, further passageway means in said cylinder component for injecting a hydraulic material into said chamber and into another space, one side of which is at least part of an outer face of said piston component, injection of said hydraulic material through said further passageway acting to push said piston component further into said chamber, means for retaining the combination of said cylinder component and said piston component on said end section of said roll, and zero-leakage, two-directional seals arranged between said cylinder component and said piston component at both radially inner and radially outer sides of said piston wherein during normal use of said rolling mill, said hydraulic fastener is maintained under pressure to hold said bearing member in place.
33. A rolling mill stand according to claim 1 wherein each seal is capable of sealing off hydraulic material under pressure of at least 2000 psi.
34. In a rolling mill stand having a roll, a bearing member for rotatably mounting one end of said roll and a hydraulic fastener for holding said bearing member in place comprising a hydraulic ring cylinder component having one face extending generally perpendicular to the roll axis and an inner cylindrical surface adapted to fit onto an end section of said roll, a chamber extending about the circumference of and located in said cylinder component and open at said one face, a hydraulic ring piston component slidably received in said chamber and having an inner face, passageway means in said cylinder component for injecting a hydraulic material into said chamber and into a space formed between said inner face of said piston and an opposing face of said chamber, means for retaining the combination of said cylinder component and said piston component on said end section of said roll, and zero-leakage two-directional seals arranged between said cylinder component and said piston at both radially inner and radially outer sides of said piston, each seal capable of withstanding pressure of at least 2000 psi wherein during normal use of said rolling mill, said hydraulic fastener is maintained under hydraulic pressure to hold said bearing member in place.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA000559281A CA1311377C (en) | 1988-02-18 | 1988-02-18 | Hydraulic nut arrangement |
| US07/598,779 US5029461A (en) | 1988-02-18 | 1990-10-18 | Hydraulic fastener |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA000559281A CA1311377C (en) | 1988-02-18 | 1988-02-18 | Hydraulic nut arrangement |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1311377C true CA1311377C (en) | 1992-12-15 |
Family
ID=4137479
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000559281A Expired - Lifetime CA1311377C (en) | 1988-02-18 | 1988-02-18 | Hydraulic nut arrangement |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA1311377C (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112178003A (en) * | 2020-09-16 | 2021-01-05 | 马鞍山钢铁股份有限公司 | Temper mill roller cylinder working roll locking device and assembling method thereof |
-
1988
- 1988-02-18 CA CA000559281A patent/CA1311377C/en not_active Expired - Lifetime
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112178003A (en) * | 2020-09-16 | 2021-01-05 | 马鞍山钢铁股份有限公司 | Temper mill roller cylinder working roll locking device and assembling method thereof |
| CN112178003B (en) * | 2020-09-16 | 2023-07-21 | 马鞍山钢铁股份有限公司 | Working roll locking device of leveling machine bending roll cylinder and assembly method thereof |
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