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Publication numberUS3768203 A
Publication typeGrant
Publication date30 Oct 1973
Filing date26 Jan 1972
Priority date26 Jan 1972
Also published asCA979033A1
Publication numberUS 3768203 A, US 3768203A, US-A-3768203, US3768203 A, US3768203A
InventorsE Bellucci
Original AssigneeAmsco Ind Co
Export CitationBiBTeX, EndNote, RefMan
External Links: USPTO, USPTO Assignment, Espacenet
Closure operating structure
US 3768203 A
Abstract
Closure movement assembly providing linear movement of a closure member in a direction transverse to a chamber opening so as to move the closure member into or out of locking position and, also providing in series, rotational movement to swing the closure member away from or toward the chamber; such dual movement of the closure member being provided with a single uninterrupted drive motion.
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Description  (OCR text may contain errors)

United States Patent [1 1 Bellucci Oct. 30, 1973 1 CLOSURE OPERATING STRUCTURE [75] Inventor: Edward A. Bellucci, Erie, Pa.

[73] Assignee: Amsco Industrial Company, Erie,

[22] Filed: Jan. 26, 1972 [21] Appl. No.: 220,789

[52] US. Cl..... 49/254, 49/340, 220/38 [51] Int. Cl E05d 15/58 [58] Field of Search 49/246, 253, 254,

[56] References Cited UNITED STATES PATENTS 10/1961 Wilmer 49/256 X 1/1970 Clements et a1. 49/246 l/l970 Beecher 220/38 FOREIGN PATENTS OR APPLICATIONS P15,447 9/1956 Germany 49/254 1,040,247 5/1953 France ..220/38 Primary ExaminerKenneth Downey Attorney-Shanley and O'Neil 5'7 7 ABSTRACT Closure movement assembly providing linear movement of a closure member in a direction transverse to a chamber opening so as to move the closure member into or out of locking position and, also providing in series, rotational movement to swing the closure member away from or toward the chamber; such dual movement of the closure member being provided with a single uninterrupted drive motion.

19 Claims, 8 Drawing Figures PATENTED 0U 30 I973 sum 3 OF 3 CLOSURE OPERATING STRUCTURE This invention is concerned with closure operating structure and, in its more specific aspects, with a hinge assembly means providing both linear movement and rotational movement of a closure from a single drive source.

Chambers requiring frequent access, and pressure operated i.e. at a vacuum or above atmospheric pressure, generally require sturdy construction interconnecting the chamber means and the closure means with interlocking means about at least a portion of the periphery of the closure 'in order to withstand the pressures involved and provide for proper locking and sealing. The locking can require some relative movement between the closure member and the chamber when the closure member is contiguous with the chamber opening for purposes of engaging or positioning for engagement flanges, edge slots, or other locking means.

It has been found that autoclave structures requiring swinging door access and linear movement for interlocking purposes lead to complexity in support and guide structures, multiple step opening procedures, and/or require multiple drives to effect proper movement or sealing.

The invention circumvents such difficulties in providing a sturdy, simplified, hinging structure providing both linear movement for interlocking purposes and swinging movement for access purposes from a single drive source. The result is a simplified, durable, easyoperating structure providing rapid actuation for both swinging and interlocking purposes.

Other advantages will be brought out in describing specific embodiments of the inventive concepts of the present invention as illustrated in the accompanying drawings.

In these drawings:

FIG. 1 is a plan view, partially in section, embodying the invention showing a chamber with its closure member in interlocking relationship with a chamber,

FIG. 2 is a similar plan view of the structure of FIG. 1 with the closure member shown out of interlocking position ready for rotational movement to swing the closure to an open position,

FIG. 3 is a similar plan view of the structure of FIGS. land 2 with the closure member in partially swung open position,

FIG. 4 is an enlarged view of a portion of the structure of FIGS. 1 2 and 3 showing releasably interconnectable structure operable between the closure member and the hinge assembly,

FIG. 5 is a plan view of a bell crank structure forming part of the present invention,

FIG. 6 is an elevational viewof the structure of FIG. 5,

FIG. 7 is a front elevational view of closure structure of the general type shown in FIG. 1 with auxiliary locking means, and

FIG. 8 is an enlarged view of wedge locking means as' used in the structure of FIG. 7. g

The plan view of FIG. 1 shows a closure member in locking position with respect to a chamber opening.

Chamber 10, only a portion of which is illustrated, in-

cludes side walls 11 and 12. Door 14 closes anopening in the frontal portion of chamber Gasket structure 15 establishes contact between the closure member and the chamber opening.

The door 14 is held in locking position by wedge members such as 16, 17 and 18, 19 on side flanges of the door and chamber. Chamber flange support takes the form of an angled member 20 at the left forward edge of the chamber shown and, at the opposite side of the chamber opening, a rearwardly projecting flange member 21 supports wedge member 19. Wedge member 18 is supported by door flange support arm 23 and, at the opposite side of the door, wedge 16 is supported on door edge flange 24. Interaction of such flange members, or other locking means, will be considered in more detail in later description.

Door 14 is supported through a hinge crank means comprising bell crank 26. The bell crank includes a fixed position fulcrum 28, input arm 29, and output arm 30. The fixed position of fulcrum 28 is established by rigid support structure 32 attached to the chamber side wall 12 but this support can be obtained from other rigid structure having a fixed positional relationship to the chamber opening. Fulcrum 28 is pivotally mounted on rigid structure arm 34.

Hinge arm 35 interconnects closure member 14 with crank output arm 30. Bracket 36 on door 14 is mounted centrally to provide sturdy support for the door; preferably it is mounted contiguous to the center of gravity of the door. Pin 37 at bracket 36 provides for at least limited pivotal movement of the hinge arm 35 with respect to the panel of door 14. At the opposite end of the hinge arm 35, the bell crank output arm 30 and the hinge arm 35 are pivotally connected at pin 38.

Power for movement of the door originates or, at least is transmitted, from a single source. In a simplified embodiment, a mechanical drive such as a fluidoperated cylinder 40 (shown in broken lines) is utilized. Outer crank input means, such as a gear drive connected to the shaft of crank 26 could be substituted for cylinder 40. Drive cylinder 40 is mounted on chamber 10, or chamber framing, by bracket 41. The mounting includes a pivotal connection 42 for limited angular movement of the cylinder. Cylinder 40 has a straight power stroke but limited angular movement for the cylinder' is provided because of the angular movement of bell crank input arm 29 about the fixed fulcrum 28. The working end of piston rod 44 is pivotally connected to the bell crank input arm'29 at pin 46.

In FIG. 1 piston rod 44 is in its extended position which through bell crank output arm 30 and hinge arm 35 has moved door 14 linearly across the closure opening (to the left as shown) into locking position.

For purposes of opening door 14, piston rod 44 is withdrawn into cylinder 40. In the plan view shown, bell crank input arm 29 moves to the left about fulcrum 28 and bell crank output arm 30 moves to the right. This action, through hinge arm 35, moves the door 14 linearly across the chamber opening to the position shown in FIG. 2. Such linear movement of the door is provided when the door is in contiguous relationship to Additional means for releasably interlocking the door 14 and bell crank 26 for swinging movement is provided through prong 52 which is mounted on door 14. This pring fits into bell crank recess 54 upon linear movement of door 14 into position for swinging open so thatboth the crank arm and door swing together. This releasable interlocking structure is shown in greater detail in FIG. 4. I

Such interlocking for swinging movement can also be carried out by limiting the pivotal movement at pin 37 where hinge arm 35 connects to the door 14. If the pivotal movement at this point is limited to the slight angular relative movement at pin 37 as required to allow for and provide the linear movement of door 14 through hinge arm 35, swinging movement will take place when the door has moved to its unlocked position. A stop or other means located at bracket 36 can lock the door and hinge arm for swinging movement. Stop block 56 on output arm 30 stops arm 35 from being swung further in a clockwise direction, by spring 48, when the door 14 has been moved to the right and interlocked for swinging movement. Stop block 56 is adjustably mounted on output arm 30.

Note in FIG. 2 that the flange means have been moved out of locking position so that the door is free for rotational movement, i.e. to be swung open. With the interlocking of door 14 and bell crank 26, continued rotation of crank 26 by withdrawal of piston rod 44 into cylinder 40 causes door 14 to swing open about fixed fulcrum 28 to a position such as that shown in FIG. 3. Reversing the action of cylinder 40, i.e. extending piston rod 44 reverses the action. The door 14 is swung into closing position (as in FIG. 2) contiguous to the chamber opening. Continued rotation of crank 26 by extension of piston rod 44 causes the door 14 to move linearly into locking position (FIG. 1). Linear movement is stopped by limit switch 57 which stops drive from cylinder 40. Other means, including mechanical stop means can be used in place of or in conjunction with limit switch 57.

Note that the in-series dual motion of the closure member is brought about by the continued rotation of the crank means in the same direction without need of interruption of motion nor direction of such motion during the separate movements of the door.

Details of the specific embodiment of the crank means, bell crank 26, are shown in FIGS. and 6. The length of hell crank shaft 60 and the number of hinge arm sockets, such as 61, 62, can be varied to suit the weight and dimensions of the closure member.

The dual movement hinge assembly structure provides unusual advantages in sturdier construction and in the adaptability to a single, unidirectional-drive means. The coordinated rotational and linear movements provided are especially advantageous in facilitating locking and sealing of pressure vessels. After the closure member has swung into place the linear movement can move the door into locking position and/or such linear movement can itself complete locking. As an example of the latter, by having the interacting wedge surface positioned as shown in FIG. 2, their interaction upon linear movement causes the door to be moved into sealing relationship, that is, toward the chamber opening. This type of wedge interaction activated by linear movement is especially suited for vacuum seal applications, lighter weight structures, and embodiments using inflatable sealing gaskets.

The rotational and linear movement in series permits clearance for top and bottom edge interlocking means during swinging of the door. For example, flange projections can be moved into alignment upon linear movement of. the door and flange mounted wedge surfaces can act to hold the closure member to the chamber along the top and bottom edges. An example of this arrangement for top and bottom edge sealing support is shown schematically in dotted lines in FIGS. 1 and 2. In FIG. 1 the chamber wedge surface 66 is shown contacting a wedge surface on door flange 68, thus moving and holding the door to the chamber opening. Whereas, in FIG. 2 the interacting wedge surfaces are separated by the linear movement of door 14, such separation allowing for swinging movement of the door.

For heavy-duty high-pressure type chambers, where it is desired to interlock the closure member and the chamber and mechanically effect sealing, the coordinated linear movement of the closure member moves and holds the closure member in position for locking. For example, the apparatus of FIG. 7 uses vertically spaced flange wedges on the sides of the door and opening. After door 70 is moved into position for locking, auxiliary locking means, with power drives 72 and 74, move the locking wedges carried on locking shaft means 76, 78 (shown in dotted lines) at the sides of the closure structure.

A mechanical type of locking and sealing action is described in detail in the patent referred to above US. Pat. No. 3,490,641. However, for purposes of understanding the present invention, as shown in the enlarged view of cooperating wedge surfaces in FIG. 8, wedge 80 moved downwardly by shaft 82 acts against wedge 84 carried by door 70. This action causes door 70 to move toward the chamber with intermediate gasket means sealing the closure. The coordinated rotational and linear movements enables such wedge surfaces to be moved out of and into interacting relationship for unlocking and for locking and sealing purposes.

As shown in FIG. 7, brackets 86 and 88 along the bottom edge of the opening support the door during the downward movement of the auxiliary locking shaft means on each side of the closure structure and thus help avoid strain being placed on the hinge assembly. The drive means 72 and 74 can be conventional fluidoperated cylinders.

Other sealing means and other flange locking means, such as cam-operated structures can be used. Also, other drive means and other configurations of the structural elements described can be resorted to in the light of the concepts and embodiments disclosed and explained. Therefore, the scope of the invention is not to be limited to the specific description but is to be determined by the scope of the appended claims.

It is claimed:

1. Closure operating structure including chamber means having an opening,

closure means for closing the opening of the chamber 7 to move rotatably to swing the closure means toward or away from the chamber, the hinge assembly means including crank means including an output arm means positioned for angular rotation about a fulcrum means,

support means for establishing a fixed position for the fulcrum means in relation to the chamber means such that the crank output arm means moves rotationally without need for interruption of movement or direction of such movement to produce both the linear and swinging movement of the closure means,

hinge arm means interconnecting the closure means and the crank output arm means for transmitting output force for movement of the closure means in relation to the chamber means,

drive means connected to the crank means for moving the crank output arm means pivotally about the fixed position fulcrum means,

retention means urging the closure means toward the chamber means when the closure means is in contiguous relationship to the opening of the chamber means, and

means releasablyinterconnecting the closure means and the hinge assembly means.

2. The combination of claim 1 in which the drive means comprises power transmitting means operating with a single uninterrupted power stroke to move the closure means serially through both linear and rotational movements. 3. The combination of claim 2 including limit means to limit linear movement of the closure means when in contiguous relationship to the chamber opening. 4. The combination of claim 3 in which the crank means comprises bell crank means having an input arm means with the input arm means and the output arm means being rigidly connected for coordinated rotation about the fixed position fulcrum means. 5. The combination of claim 4 in which the single stroke drive means comprises a fluid operated work cylinder having piston rod means pivotally connected to' the bell crank input arm means, with the work cylinder being mounted for limited pivotal movement to allow for curvilinear movement of such piston rod connection with the bell crank input arm means about the fixed position bell crank fulcrum means. 6. The combination of claim 1 in which the hinge arm means comprises a rigid elongated arm pivotally connected to the crank output arm means and connected to the closure means. 7. The combination of claim 6 in which the hinge arm means is connected centrally of the closure means for support of the closure means. 8. The combination of claim 8 in which the hinge arm means is connected to the closure means contiguous to a location for center of gravity support of the closure means.

9. The combination of claim 1 including means for releasably interconnecting the closure means and the crank output arm means upon linear movement of the closure means in a direction toward the fulcrum means, with the retention means exerting a directional moment of force urging the closure means toward the fulcrum means.

10. The combination of claim 9 in which the means for releasably interconnecting the closure means and the crank output arm means is mounted on the closure means and interacts with the crank means.

11. The combination of claim 10 in which the means for releasably interconnecting the closure means and the crank output arm means comprises an elongated prong means mounted on the closure means and tapered at one longitudinal end to interfit with a tapered recess in the crank output arm means upon linear movement of the closure means in a direction toward the fixed position fulcrum means.

12. The combination of claim 1 in which the retention means is connected to the hinge arm means.

13. The combination of claim 12 in which the retention means comprises spring means interconnecting the hinge arm means and the crank means.

14. The combination of claim 12 including stop block means mounted on the crank output arm means and acting to limit angular movement of the hinge arm means in relation to the crank output arm means.

15. The combination of claim 1 including means carried on the closure means and means positioned about the opening of the chamber means for interlocking the closure means and the chamber means.

16. The combination of claim 16 in which the means carried on the closure means and positioned about the opening of the chamber means comprises cooperating flange means.

17. The combination of claim 16 in which the linear movement of the closure means imposed by the crank means causes relative movement between the flange means on the closure means and the cooperating flange means on the chamber means establishing alignment of such flange means to permit sealing between the closure means and the chamber means.

18. The combination of claim 16 further including auxiliary locking means for effecting a pressure-tight seal between the closure member and the chamber opening.

19. The combination of claim 1 in which the chamber means comprises a pressure-operated sterilizing vessel.

Patent Citations
Cited PatentFiling datePublication dateApplicantTitle
US3004303 *29 Jun 195917 Oct 1961Vickers Armstrongs AircraftDoors for the fuselages of pressurized aircraft
US3488883 *8 Aug 196813 Jan 1970Welding & Steel Fabrication CoSealed door leveling system
US3490641 *27 Feb 196820 Jan 1970American Sterilizer CoPressure vessel closure and closure fastener
*DE15447C Title not available
FR1040247A * Title not available
Referenced by
Citing PatentFiling datePublication dateApplicantTitle
US3918204 *4 Jan 197411 Nov 1975Dolney Theodore JGate assembly
US4192435 *26 Mar 197911 Mar 1980Aluminum PechineySelf-sealing closure device for transport tank
US4228134 *13 Oct 197714 Oct 1980The Goodyear Tire & Rubber CompanyAutoclave for thermally treating very long rubbery hose products, and the like
US4262447 *20 Aug 197921 Apr 1981Sybron CorporationDouble acting hinged pressure vessel closure
US4611555 *29 Mar 198316 Sep 1986Burford Corp.Spreader for particulate material
US4666551 *17 Jun 198519 May 1987Thaddeus SoberayVacuum press
US4715315 *7 Nov 198529 Dec 1987Burford Corp.Dispenser for particulate material
US4932160 *4 May 198912 Jun 1990Sterilizer Technologies CorporationClosure apparatus and method
US5361926 *12 Oct 19938 Nov 1994Krauss Maffei AktiengesellschaftCover for centrifuge housing
US707688810 Mar 200418 Jul 2006The Boc Group, PlcFreeze dryer
US8066140 *28 Feb 200329 Nov 2011The Charles Machine Works, Inc.Container door and container door latching and sealing system
US866771721 Dec 201211 Mar 2014Mclaughlin Group, Inc.Digging and backfill apparatus
US20110163109 *2 Sep 20097 Jul 2011Lokaway Pty. Ltd.Security box
USB430798 *4 Jan 197428 Jan 1975 Title not available
DE2717232A1 *19 Apr 19772 Nov 1978Calor Emag Elektrizitaets AgTuer fuer eine schaltanlagenzelle
DE29614557U1 *22 Aug 199618 Dec 1997Niemann Hans DieterDreh-Kippfenster oder -Tür
EP0068157A1 *29 May 19825 Jan 1983AUTE Gesellschaft für autogene Technik mbHFireproof closure
EP1549817A1 *8 Oct 20036 Jul 2005Lokaway Pty Ltd.Security door and frame construction
WO1984003941A1 *27 Mar 198411 Oct 1984Burford CorpSpreader for particulate material
Classifications
U.S. Classification49/254, 49/340
International ClassificationE05D3/02
Cooperative ClassificationE05D3/022, E05Y2900/20
European ClassificationE05D3/02B