WO1987007051A1 - Suspension a bras de liaison - Google Patents

Suspension a bras de liaison Download PDF

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Publication number
WO1987007051A1
WO1987007051A1 PCT/US1987/000639 US8700639W WO8707051A1 WO 1987007051 A1 WO1987007051 A1 WO 1987007051A1 US 8700639 W US8700639 W US 8700639W WO 8707051 A1 WO8707051 A1 WO 8707051A1
Authority
WO
WIPO (PCT)
Prior art keywords
bore
disposed
opening
shaft
link arm
Prior art date
Application number
PCT/US1987/000639
Other languages
English (en)
Inventor
Gary Butts
Original Assignee
Mechanical Technology Incorporated
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mechanical Technology Incorporated filed Critical Mechanical Technology Incorporated
Publication of WO1987007051A1 publication Critical patent/WO1987007051A1/fr

Links

Classifications

    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05D—HINGES OR SUSPENSION DEVICES FOR DOORS, WINDOWS OR WINGS
    • E05D3/00—Hinges with pins
    • E05D3/06—Hinges with pins with two or more pins
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M7/00—Vibration-testing of structures; Shock-testing of structures
    • G01M7/02—Vibration-testing by means of a shake table
    • G01M7/04—Monodirectional test stands

Definitions

  • the present invention relates to the field of mechanical shakers and more specifically to electromagnetically driven armature shakers.
  • shakers are used to mechanically shake an item for the purpose of diagnostically testing responses to certain driving forces.
  • the item is physically attached to a moving portion of a shaker and when the shaker is activated, the item is subjected to a variety of test conditions.
  • the moving portion of the shaker is typically driven by a force which may be continuous, cyclical or impulsed.
  • a housing unit contains a stationary field coil which is connected to an external power source.
  • a freely moving armature located within the housing contains an armature coil which is driven by a power amplifier.
  • the armature coil is fixed to the shaking portion if the unit, such as an armature frame.
  • the armature By providing a varying drive signal from the amplifier to the armature coil, the armature will respond and move accordingly due to a change in the electromagnetic field.
  • the size and direction of the shaker force being determined by the strength of the driving signal from the power amplifier and the power applied to the stationary field coil.
  • a variety of platforms or tables are normally coupled to the armature, wherein the item to be subjected to testing is mounted onto the table by fixed means, such as bolts, screws, etc.
  • the platform or table is usually constructed from a hard substance, such as metal, to prevent deformation of the platform which will interfere with the resultant testing.
  • One side-effect from using such an armature frame is the generation of unwanted frequency components from the mechanical movement of the shaker armature. These unwanted frequencies are generated as a result of oscillations created within the moving metal. Such osillations finally reach a peak resonant frequency of the particular material in motion and tend to have disruptive effects by producing undesirable additional factors during the testing cycle.
  • a number of types of resonance are encountered in prior art armature frames. ' One is the telescoping resonance associated with the height of the table and the other is the bending resonance associated with the mass/stiffness distribution of the table.
  • a further problem is associated with means to 15 stabilize the shaker armature during operation.
  • an armature shaft is smaller in diameter in comparison to the diameter of the armature.
  • some retainer means are needed to support the armature.
  • Prior art methods have used springs and 2 0 rubber bushings, if any support were used at all.
  • a fixed field winding and a moveable armature provide the electrodynamic coupling for axially moving an armature table which is fixed to the armature coil.
  • the armature assembly is held in position by a center shaft.
  • the shaft is placed within a recirculating bearing which provides a low coefficient of friction when the armature is driven.
  • the armature frame is comprised of flat, circular, thin upper and lower plates and a middle-section between the two plates.
  • the height of the armature frame in the armature raises any telescoping resonant frequencies encountered.
  • the bending resonant frequencies are effectively shifted above the testing spectrum of frequencies also by the laminated design of the armature frame.
  • the top and bottom plates are constructed of materials having a higher modulus of elasticity, while the middle-section is constructed from materials having a lower density.
  • the recirculating bearing includes a housing which includes a plurality of return channels located concentric to the inner wall of the housing.
  • a plurality o balls are positioned between the shaft and inner wall of the housing, as well as in the channels.
  • Top and bottom retainers having recessed areas which permit the balls to move from the interior position next to the shaft to one of the channels, are placed to enclose the balls within the housing.
  • the bearing may also be used for rotational movement of the shaft.
  • a linkage system attached to the upper portion of the armature and the shaker housing reduces wobble of the armature.
  • the linkage system is comprised of a plurality of link arms.
  • Eack link arm includes two end members coupled to a common center member, wherein the three members provide three pivoting points in an axial direction of the shaft, but prevent any lateral movement.
  • the pivoting action of the link arm further compensates for the change in the physical distance of the shake table from the shaker housing support as it moves axially.
  • Figure 1 is a pictorial view showing component elements of a shaker apparatus of the present invention.
  • FIG. 1 is a cross-sectional view of the shaker apparatus of Figure 1.
  • Figure 3 is an enlarged cross-sectional view of a portion of a Figure 1 showing a placement of a bearing of the present invention.
  • Figure 4A is a cross-sectional view of an armature frame of the present invention which is shown in Figure 1.
  • Figure 4B is a plan view of an armature coil of the present invention which is shown in Figure 1.
  • Figure 5A is a pictorial view of a link arm of the present invention.
  • Figure 5B is a split pictorial view of the link arm of Figure 5A.
  • Figure 6A is a cross-sectional view of the link arm of Figure 5A showing its static state.
  • Figure 6B is a cross-sectional view of the link arm of Figure 5A showing the elongated state in a first direction.
  • Figure 6C is a cross-sectional view of the link arm of Figure 5A showing its elongated state in a second direction.
  • Figure 7 is a pictorial view of a bearing housing of the present invention.
  • Figure 8 is a top plan view of the bearing housing of Figure 7.
  • Figure 9 is a pictorial view of the bearing housing of Figure 7, top and bottom bearing retainers and a shaft which is inserted into the bearing housing.
  • Figure 10 is a cross-sectional view of an assembled bearing shaft, and placement of balls within the bearing housing.
  • armature type shaker having an improved armature frame, a recirculating ball bearing and link arm suspension system is described.
  • numerous specific details are set forth such as specific thicknesses, etc. in order to provide a thorough understanding of the present invention. However, it will be apparent to one skilled in the art that the present invention may be practiced without these specific details. In other instances, well-known structures have not been described in detail in order not to unnecessarily obscure the present invention.
  • a housing 11, having an outer ring 12 and inner ring 13 houses field winding 14 which resides in concentric circles between the two rings 12 and 13.
  • Housing 11 has center opening 16 which houses bearing 17 and armature shaft 18.
  • a circular cover 15 in shape of a ring is placed onto housing 11 to enclose field winding 14.
  • Cover 15 rests atop ring 12 and over field winding 14 leaving opening 19 such that the combination of ring 12 and 15 is at approximately equal height as ring 13.
  • the material construction of housing 11, cover 15 and field winding 14 are well-known in the prior art.
  • An armature coil assembly 20 comprised of a circular looping of armature winding 21 is inserted into opening 19.
  • Armature coil 20 resides within a circle formed by field coil 14 and cover 15, and ring 13 resides within armature coil 20.
  • Armature coil 20 does not physically touch members 13, 14 and 15 so that armature coil 20 may freely move in an axial direction (up and down in the drawing) within opening 19.
  • By applying a varying driving signal to the armature coil 20 it can move " (shake) in response to the driving signal in an axial direction shown by arrows 22.
  • a variety of prior art armature coils may be used for armature coil 20, however, in the present invention a special armature coil 20 was designed to mate directly onto armature frame 30.
  • FIG 3 is an enlargement of a portion of Figure 2 and illustrates the placement of members within central openings 16.
  • armature coil 20 is supported to housing 11 by center shaft 18 and bearing 17.
  • the shaft 18 has an upper lip 23 which is bolted onto the center hub 26 of armature frame 30 by bolts 27. It will be noted that, alternatively, bolts 27 may be reversed such that the bolts are inserted from the top of the armature frame, through center hub 26 and upper lip 23.
  • the shaft 18 is inserted into central opening 16 of housing 11.
  • a bearing 17 having recirculating balls 31 makes contact with a portion of the shaft 18.
  • a bottom shaft member 32 of the shaft 18 fits into diaphragm 33 which is made from a flexible material, such as rubber. Diaphragm 33 is held in place between support members 35 and 36 which are joined together by bolt 37. Diaphragm 33 also has a raised portion 34 which surrounds
  • bearing 17 is held in place by bearing support 0 members 42 and 43 which clamp the bearing 17 such that balls 31 make contact with shaft 18.
  • Bearing support members 43 is coupled to support member 36 by bolts 44 and bearing support member 42 is coupled to ring 13 of housing
  • 44 and 45 may be of a variety of commercially available bolts.
  • a constant DC voltage is impressed across field winding 14 and a varying driving signal is impressed across armature winding 21 to control the force generated in armature coil 20 (control lines and amplifiers are not shown in the drawing).
  • the armature frame 30 which is fixed onto the armature coil 20 moves in unison to the armature coil 20.
  • the shaft 18 attached to the armature frame 30 moves within bearing 17 wherein bearing 17 provides a low friction of mechanical coupling of shaft 18 to housing 11.
  • a link arm 46 is used to restrict any movement other than in the axial direction. Although only three link arms 46 are shown in the drawing, any number greater than one, may be used. Each of the link arms 46 is fixed onto armature frame 30 and also to individual stanchions
  • a degauss coil 49 is attached to the inside of cover 48 and provides reduced stray magnetic field above armature frame 30.
  • Armature frame 30 is comprised of a top plate 51, bottom plate 52 and middle section 53.
  • the preferred embodiment utilizes circular plates 51 and 52, however, the shape of the plates 51 and
  • Plate 51 may be adapted to meet other shaker designs.
  • Plate 51 includes tapped openings 54 for bolting on items to be shaken.
  • the middle section 53 is also of a circular shape such that upper portion 55 couples to top plate 51 and lower portion 56 couples to bottom plate 52.
  • Middle section 53 has a hollow core 57 and ribs 58 about the outer periphery.
  • the area 59 between the ribs are devoid of any material to allow middle section 53 to basically have a ribbed design.
  • the preferred embodiment has the top plate 51 of a larger diameter than bottom plate 52.
  • the middle section 53 has the upper portion 55 and lower portion 56 at different diameters to correspond to plates 51 and 52, respectively. Ribs 58 are tapered to compensate for this difference in diameter.
  • the two plates 51 and 52 are coupled to mid-section 53 by bolts 60 and adhesive, although any other equivalent fastening system will work.
  • the armature coil 20 is coupled to bottom plate 52 also by bolts 61. When mounted together, armature frame 30 and armature coil 20 are a single unit as shown in Figure 1.
  • the frame 30 is constructed to have a table height 62 which is shorter than prior art tables.
  • the singular design of combining armature frame 30 and armature coil 20 also reduces the physical height of the moving elements from prior art armature coil and frame combinations, thereby further ' aiding in raising the frequency of telescoping resonance.
  • the shorter height 62 raises the frequency of the telescoping resonance so that the telescoping resonance lies above the test frequency range and does not interfere with the testing.
  • a bending resonance associated with the mass and physical properties of the materials become more significant. The bending resonance has the effect of non-uniform acceleration at different points of the frame- 30, thereby causing distorted test readings.
  • the frame 30 of the present invention does not completely remove the bending resonances, but instead increases the resonant points to frequencies which are higher than the test spectrum. Most shaker testing is achieved within a frequency spectrum of D.C. to 2000 Hertz. Typical prior art armature frames, especially those having shortened height (as in the case of the table 30 of the preferred embodiment), will have bending resonances within the D.C. to 2000 Hertz spectrum. The design of the present invention causes these bending resonance frequencies to shift to a point above this spectrum. Ideally such frequency shifting is achieved by using a low density-high elastic material, such as beryllium, but the cost is usually prohibitive for commercial sales of beryllium armature frame.
  • the frame 30 of the present invention achieves this shifting of the bending resonant frequencies by utilizing a laminated design which has a higher modulus material on the outside and a lower density honey-combed material on the inside.
  • a laminated design which has a higher modulus material on the outside and a lower density honey-combed material on the inside.
  • the armature frame 30 uses a thin top ' plate 51 which has a thickness of approximately 1/8 inch at the outer edge 63 and 1 inch near the center 64.
  • Bottom plate 52 is also thin having a thickness of approximately 1/8 inch at the outer edge 65 and 1 inch near the center 66.
  • the plates 51 and 52 have tapered thicknesses to provide more bending support in the center 64 and 66.
  • the plates 51 and 52 have a high Young's modulus of elasticity while the middle section 53 is constructed of material having low density.
  • the preferred embodiment uses steel for plates 51 and 52 and magnesium for section 53. It is known that magnesium, steel and aluminum have approximately the same density to modulus ratio which results in the three materials having approximately the same resonant frequencies. Steel was chosen for plates 51 and 52 due to its higher Young's modulus while magnesium was chosen for middle section 53 for its low density.
  • Use of the multi-materials construction in combination with the tapered ribbed design of middle section 53 shifts the resonating points of frame 30 bending resonances to frequencies above the 2000 Hertz test spectrum.
  • the design of the preferred embodiment has been finally trimmed wherein the armature frame 30 can operate up to 3000 Hertz encountering only 2 bending resonances.
  • the link arm 46 of Figure 1 is shown in more detail in Figures 5A, 5B, 6A, 6B and 6C.
  • a link arm 46 is shown comprised of a body 78, linkage 79 and brackets 83 and 84 and three cylindrically shaped shafts 75, 76 and 77.
  • Body 78 has two parallel cylindrical bores 80 and 81 along the length 82 of the body 78.
  • Body 78 has an opening 91 for exposing a portion of bore 81.
  • Body 78 also has a second opening 90 for exposing a portion of bore 80. Opening 90 is in a direction 90 degrees from opening 91.
  • the bracket 84 having a base 92 and extension 93, has a cylindrical bore 94 at the end of extension 93 opposite base 92. Extension 93 is inserted into opening 91 until bores 81 and 94 are aligned, at which point shaft 77 is slideably inserted through both bores 81 and 94 to couple bracket 84 to body 78. Shaft 77 permits body 78 and bracket 84 to rotate about the shaft 77.
  • the linkage 79 having bores 95 and 96 at each end couples bracket 83 to body 78. Bore 95 is inserted into opening 90 until bores 95 and 80 are aligned and then shaft 76 is inserted through both bores 95 and 80 to couple linkage 79 to body 78. Body 78 and linkage 79 freely rotate about shaft 76.
  • the bracket 83 having a base 97 and bore 85, has opening 98 which exposes a portion of bore 85. Opening 98 faces in the direction of opening 90 so that the other end of the linkage of bore 96 is inserted into opening 98.
  • Bores 96 and 85 are aligned to permit shaft 75 to be inserted through both bores 96 and 85 to couple bracket 83 to body 78, which freely rotate about shaft 75.
  • each end of shafts 75-77 are mounted onto bracket 83 and body 78 by bearings 70.
  • the bearings may be of any prior art high axial load bearings and are used primarily to transfer lateral loads from brackets 83 to 84.
  • bracket 83 is bolted onto plate 29 of frame 30 as shown in Figure 1.
  • Bracket 92 is bolted onto stanchions 47 of Figure 1.
  • the link arm 46 permits pivotal movement about shaft 75-77 but prohibits any lateral movement along the shafts. Therefore by positioning a plurality of link arms 46, the upper wobble of armature frame 30 is reduced.
  • the drawing of Figure 1 shows only three such link arms but any number greater than one may be used. If only two link arms 46 are used, the two must be placed in such a way so that a pivotal movement of one link arm is opposed by the lateral positioning of the second link arm (that is, the two link arms must not be placed 180 degrees apart) .
  • Figures 6A, 6B and 6C illustrate another advantage of the link arm 46.
  • Figure 6A shows the static state of link arm 46 having axes 88 and 89 at right angles to each other.
  • Figure 6B illustrates the foreshortening encountered.
  • Link arm 46 by pivoting at the ' three shaft centers 71, 72 and 73 compensates for the foreshortening without placing additional load on the armature frame 30.
  • Axis 88 shifts to 88A and axis 89 shifts to 89A.
  • Figure 6C illustrates the alternative case where armature frame 30 moves in the opposite direction and again encounters foreshortening.
  • Link arm 46 compensates again by shifting axis 88 to 88B and axis 89 to 89B.
  • the link arm 46 is presented to alleviate the foreshortening problem encountered on shake tables, it is readily apparent that the link arm may be used in other applications without departing from the spirit and scope of the invention. Also, the materials used for constructing the link arm is of metal in the preferred embodiment, however, any of a variety of materials may be used.
  • Body 100 is circular in shape and has a bearing housing 101 surrounding an
  • Interior channel element 102 and in turn is surrounded externally by casing 103.
  • Interior channel element 102 includes a plurality of elongated return channel openings 104, which pass completely through element 102. Further, element 102 is recessed below the two end surfaces 105 of -, - housing 101.
  • bearing body 100 is shown with retainers 106 and 107 and shaft 109. Once the shaft 109 has been inserted through the bearing 17, retainer 107 is fixed to housing 101 by screws (not
  • housing 101 having tapped holes 108 for accepting the screws. Then spherical balls 110 are inserted into channels 104 and between shaft 109 and interior element 102 as shown in Figure 10.
  • retainers 106 and 107 are designed to correspond to
  • shaft 109 is shown surrounded by a plurality of balls 110.
  • the balls 110 will also roll in relatively the same 30 direction, thereby presenting a lower coefficient of friction to shaft 109.
  • balls 110 first move along a wall 114 and recirculates through channels 104 as shown by arrows 113. The recirculation is possible because the retainers 106 and 107 have recessed areas 121, as well as shortened inner wall 122, which operate in conjunction with recessed portions 123 of element 102 to permit the balls 110 to freely move as shown by arrows 113.
  • Balls 110 are also capable of providing a low friction surface when the shaft 109 is moved in a rotational direction. Balls 110 will move in a rotational direction as the shaft 109, as shown by arrows 115. Therefore, the shaft 109 may move linearly, rotationally, or a combination of the two motions.
  • the design of the bearing 17 allows any given ball 110 to cycle through any of the channels 104.
  • the load transfer is accomplished by the balls 110 in contact with the shaft 109 and stanchions 120 which are located between channels 104.
  • the arrows 111 and 112 show the route of the load transfer from shaft 109 to housing 101.
  • a significant advantage of this design resides in its ability to simultaneously perform as a low friction bearing for both linear and rotational movement of the shaft.
  • the shaker of the preferred embodiment only moves linearly, the use of the bearing is not constrained to this specific application.
  • the bearing of the present invention allows more shaft surface area contact with balls 110 allowing for a more even distribution of the load transfer from the shaft 109 to bearing 17.
  • the load transfer 111 is accomplished across a larger number of balls 110 than prior art bearings.
  • the larger number of balls 110 making contact to shaft 109 permits higher load ratings or for the same rating, allows the balls 110 to be constructed of lighter load bearing material, such as plastic, whereas prior art designs required higher load transfer requirements per ball for a given diameter shaft.

Abstract

Un système de suspension permet de commander le mouvement d'un premier (11) et d'un second (30) organe ayant un mouvement alternatif l'un par rapport à l'autre. Le système de suspension comprend plusieurs bras de liaison (46) couplés entre les premier (11) et second (30) organes alternatifs, au moins l'un des bras de liaison (46) étant déplacé par rapport à au moins un autre pour obtenir une relation autre qu'une relation d'opposition diamétrale. Chaque bras de liaison (46) comprend un corps (78) ayant une première et une seconde extrémité, des premiers moyens de liaison (84, 92, 93) pour coupler par pivotement une extrémité du corps (78) à l'un des organes à mouvement alternatif relatif, et des seconds moyens de liaison (83, 79) pour coupler par pivotement l'autre extrémité du corps (78) et l'autre organe à mouvement alternatif relatif. Le mouvement des premier et second organes à mouvement alternatif relatif est possible uniquement le long de l'axe du mouvement alternatif.
PCT/US1987/000639 1986-05-05 1987-03-25 Suspension a bras de liaison WO1987007051A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US85960986A 1986-05-05 1986-05-05
US859,609 1986-05-05

Publications (1)

Publication Number Publication Date
WO1987007051A1 true WO1987007051A1 (fr) 1987-11-19

Family

ID=25331323

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US1987/000639 WO1987007051A1 (fr) 1986-05-05 1987-03-25 Suspension a bras de liaison

Country Status (2)

Country Link
EP (1) EP0268609A4 (fr)
WO (1) WO1987007051A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8713759B2 (en) * 2012-02-27 2014-05-06 Lenovo (Beijing) Co., Ltd. Hinge apparatus and electronic device comprising it

Citations (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US30587A (en) * 1860-11-06 Stop-hinge
US82658A (en) * 1868-09-29 Philip j
US459097A (en) * 1891-09-08 Connecting-rod
US727353A (en) * 1902-01-27 1903-05-05 George W Greenwood Pressure-exerting machine.
US781693A (en) * 1904-08-02 1905-02-07 John L Tandy Mirror-hanger.
US1015040A (en) * 1911-11-24 1912-01-16 Joseph Laurich Carriage-hinge.
US1096657A (en) * 1913-07-09 1914-05-12 Warren Carey Automobile-hinge.
US1672520A (en) * 1925-07-27 1928-06-05 Garrett Frederick George Door hinge
US2095192A (en) * 1936-07-17 1937-10-05 Pennsylvania Railroad Co Smoke box casing for a locomotive
DE801904C (de) * 1948-10-02 1951-01-25 Kloeckner Humboldt Deutz Akt G Getriebe fuer Brikettstrangpressen
US2642018A (en) * 1950-02-23 1953-06-16 Weeber Karl William Greenhouse ridge assembly
US2845652A (en) * 1952-09-20 1958-08-05 Ver Baubeschlag Gretsch Co Device for connecting a window sash with a window frame
US2936636A (en) * 1958-05-02 1960-05-17 Andrew J Wacht Press
US2941236A (en) * 1955-04-18 1960-06-21 Peerless Mfg Company Hinge
US2973908A (en) * 1958-06-02 1961-03-07 Bath Iron Works Corp Breaker plate release mechanism for single roll crusher
US3044292A (en) * 1958-12-17 1962-07-17 Lyle E Matthews Vibration table
US3262308A (en) * 1964-01-10 1966-07-26 Schloss Fred Vibrating table structure
US3309864A (en) * 1964-11-06 1967-03-21 Westinghouse Air Brake Co Flexible link connection
US3419238A (en) * 1967-06-21 1968-12-31 Air Force Usa Parallel platform linkages for shock isolation systems
US3832756A (en) * 1973-07-02 1974-09-03 H Lew Dual action hinge for folding doors

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1554161A (en) * 1924-06-06 1925-09-15 Richard W Hubbard Hinge

Patent Citations (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US30587A (en) * 1860-11-06 Stop-hinge
US82658A (en) * 1868-09-29 Philip j
US459097A (en) * 1891-09-08 Connecting-rod
US727353A (en) * 1902-01-27 1903-05-05 George W Greenwood Pressure-exerting machine.
US781693A (en) * 1904-08-02 1905-02-07 John L Tandy Mirror-hanger.
US1015040A (en) * 1911-11-24 1912-01-16 Joseph Laurich Carriage-hinge.
US1096657A (en) * 1913-07-09 1914-05-12 Warren Carey Automobile-hinge.
US1672520A (en) * 1925-07-27 1928-06-05 Garrett Frederick George Door hinge
US2095192A (en) * 1936-07-17 1937-10-05 Pennsylvania Railroad Co Smoke box casing for a locomotive
DE801904C (de) * 1948-10-02 1951-01-25 Kloeckner Humboldt Deutz Akt G Getriebe fuer Brikettstrangpressen
US2642018A (en) * 1950-02-23 1953-06-16 Weeber Karl William Greenhouse ridge assembly
US2845652A (en) * 1952-09-20 1958-08-05 Ver Baubeschlag Gretsch Co Device for connecting a window sash with a window frame
US2941236A (en) * 1955-04-18 1960-06-21 Peerless Mfg Company Hinge
US2936636A (en) * 1958-05-02 1960-05-17 Andrew J Wacht Press
US2973908A (en) * 1958-06-02 1961-03-07 Bath Iron Works Corp Breaker plate release mechanism for single roll crusher
US3044292A (en) * 1958-12-17 1962-07-17 Lyle E Matthews Vibration table
US3262308A (en) * 1964-01-10 1966-07-26 Schloss Fred Vibrating table structure
US3309864A (en) * 1964-11-06 1967-03-21 Westinghouse Air Brake Co Flexible link connection
US3419238A (en) * 1967-06-21 1968-12-31 Air Force Usa Parallel platform linkages for shock isolation systems
US3832756A (en) * 1973-07-02 1974-09-03 H Lew Dual action hinge for folding doors

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP0268609A4 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8713759B2 (en) * 2012-02-27 2014-05-06 Lenovo (Beijing) Co., Ltd. Hinge apparatus and electronic device comprising it

Also Published As

Publication number Publication date
EP0268609A1 (fr) 1988-06-01
EP0268609A4 (fr) 1989-02-07

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