EP1710194A2 - Cable connecting device - Google Patents
Cable connecting device Download PDFInfo
- Publication number
- EP1710194A2 EP1710194A2 EP06014420A EP06014420A EP1710194A2 EP 1710194 A2 EP1710194 A2 EP 1710194A2 EP 06014420 A EP06014420 A EP 06014420A EP 06014420 A EP06014420 A EP 06014420A EP 1710194 A2 EP1710194 A2 EP 1710194A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- tension member
- socket
- side plate
- compressive
- elevator system
- 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.)
- Granted
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Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
- B66B7/00—Other common features of elevators
- B66B7/06—Arrangements of ropes or cables
- B66B7/08—Arrangements of ropes or cables for connection to the cars or cages, e.g. couplings
- B66B7/085—Belt termination devices
Landscapes
- Lift-Guide Devices, And Elevator Ropes And Cables (AREA)
- Installation Of Indoor Wiring (AREA)
- Details Of Connecting Devices For Male And Female Coupling (AREA)
Abstract
Description
- The present invention relates to elevator systems. More particularly the invention relates to a termination for a flexible flat tension member.
- A conventional traction elevator system includes a car, a counterweight, two or more ropes (tension members) interconnecting the car and counterweights; terminations for each end of the ropes at the connection points with the car and counterweights, a traction sheave to move the ropes and a machine to rotate the traction sheave. The ropes have traditionally been formed of laid or twisted steel wire which are easily and reliably terminated by means such as compression terminations and potted terminations.
- Compression type terminations for steel ropes of larger diameters (conventional steel elevator ropes) are extremely effective and reliable. The range of pressures placed on such terminations is reasonably broad without adverse consequence. Providing that the pressure applied is somewhere reasonably above the threshold pressure for retaining the ropes, the termination is effective.
- With an industry trend toward flat ropes, those ropes having small cross-section cords and polymeric jackets, significantly more criticality is involved in effectively terminating the same. More specifically, the polymeric coating can creep to even 50% of its original thickness when subjected to pressure. Prior art knowledge which teaches one to exceed a threshold is not all that is of concern for flexible flat tension members. Upper limits on compression are also important.
- Since current knowledge in the art of tension member terminations is less than sublime for flexible flat tension members due both to the small cord diameter and the jacket properties discussed above, the art is in need of a tension member terminating device which specifically optimizes terminations of the flexible flat tension members currently emerging in the field.
- According to the present invention, a compression termination device having a friction enhancing construction while reducing compressive forces applied to the tension member, comprises a load side plate, a cut side plate and a socket, a portion of which being receivable between said load side and cut side plates and a portion of which is bulb shaped. The plates and socket are of sufficient width to accept a flexible flat tension member of a selected width and are securable together by fasteners. In a condition where the fasteners are loose, the tension member is insertable between the load side plate and socket, toward and around the bulb and back up between the cut side plate and socket whereafter tightening of the fasteners produces significant frictional forces on the tension member to retain the same while compressive forces on the tension member are intentionally limited to about 2 Mpa on the load side of the device and 5 Mpa on the cut side of the device. Friction is increased by texturing the surfaces of the termination device with which the tension member makes contact. With compressive forces as stated, creep is minimized while the termination maintains a sufficient gripping force to provide a factor of safety (fos) of 12 to maintain adequate strength of the termination.
- Since creep is a possibility even with Mpa levels at the stated limits, the invention optionally includes a structure providing resilience such that compressive force on the tension member will remain in the acceptable range ever if creep does occur.
- The termination of the invention further optionally includes a jamming device attachable to the cut end of the tension member. In the unlikely event of tension member slippage through the termination device, the jamming device will be drawn into the termination device and will prevent the tension member cut end from pulling through the termination device.
-
- FIGURE 1 is a perspective view of an elevator system;
- FIGURE 2 is an exploded perspective view of the termination device of the invention;
- FIGURE 3 is an end elevation view of a socket of the invention;
- FIGURE 4 is a side elevation view of a socket of the invention;
- FIGURE 5 is a top plan elevation view of a socket of the invention;
- FIGURE 6 is a view similar to FIGURE 3 but having studs installed therein;
- FIGURE 7 is an end elevation view of a compression plate of the invention;
- FIGURE 8 is a side elevation view of a compression plate of the invention;
- FIGURE 9 is an end elevation view of the invention in an assembled and torqued condition;
- FIGURE 10 is a side elevation view of the invention in an assembled and torqued condition;
- FIGURE 11 is a schematic view of a nut and bolt width belleville washers thereon in the uncompressed condition;
- FIGURE 12 is a schematic view of a nut and bolt width belleville washers thereon in the compressed condition;
- FIGURE 13 is a schematic view of an alternate biasing means of the invention;
- FIGURE 14 is a schematic view of the termination device of the invention illustrating force directions for calculations provided herein;
- FIGURE 15 is a perspective view of the pivot connector of the termination device of the invention;
- FIGURE 16 is a perspective assembled view of the jamming device of the invention;
- FIGURE 17 is a perspective view of the interior portion of one side of the jamming device; and
- FIGURE 18 is a perspective view of the interior portion of a second side of the jamming device.
- FIGURE 19 is a sectional, side view of a traction sheave and a plurality of flat ropes, each having a plurality of cords.
- FIGURE 20 is a sectional view of one of the flat ropes.
- Referring to FIGURE 1, the relative location of the tension member termination device of the invention can be ascertained, For clarity, the
elevator system 12 is illustrated havingcar 14,counterweight 16, atraction drive 18 and amachine 20. Thetraction drive 18 includes atension member 22 interconnectingcar 14 andcounterweight 16 which member is driven bysleeve 24. Both ends oftension member 22 i.e., car end 26 andcounterweight end 28 must be terminated. It is this termination point for a flexible flat tension member with which the invention is concerned. An exemplary tension member of the type contemplated in this application is discussed in further detail inU.S. Serial No. 09/031,108 filed February 26,1998 - Focusing on the termination device, referring to FIGURE 2, and noting that both
ends socket 30 around which a flat flexible tension member extends (not shown), aload side plate 80 and acut side plate 96. The invention further comprises a resilient compression subsystem and a pivoted connector which will be discussed hereinbelow. - Returning to the principal portion of the invention and directing attention to FIGURES 2-5,
socket 30 includes atapered end 32 to both ease insertion of a tension member in the loosely assembled condition of the device and additionally and importantly to avoid a sharp edge which would otherwise promote fatigue in the tension member where the member enters thetermination device 10. The taper is from both major surfaces ofsocket 30 i.e.,load surface 34 and cutsurface 36.Socket 30 further includestroughs Troughs bulb surface 42 thereby increasing the coefficient of friction of all surfaces ofsocket 30 with which the terminated tension member will make contact. A preferred method for texturingtroughs surface 42 is by sand blasting. It will be understood however that other methods such as machining, chemical etching, etc, could also be used. -
Socket 30 further includesbinding wings fastener clearance holes 48 and, in a preferred arrangement, a plurality ofstud receiving openings 50. The number ofholes 48 depends upon thelength socket 30 and the allowable pressure on the tension member. In the embodiment of FIGURES 3 and 4, fourholes 48, and threeopenings 50 are provided on eachwing openings 50 are threaded to receive studs 52 (FIGURE 6), It should be noted thatstuds 52, as shown in FIGURE 6 extend only toward thecut side 36 ofsocket 30.Studs 52 enable the application of a greater compressive load oncut side 36 ofsocket 30 than the load applied onload side 34 ofsocket 30 which is applied by bolts extending completely throughdevice 10. In other words, the load placed on the respective sides of socket 30 (through plates discussed hereunder) by the bolts (which extend through the device) and nuts is approximately equal;studs 52 allow more load to be placed or the cut side as is desirable and explained further hereinafter. - In a preferred embodiment, socket 30 (the section bound between the plates) is about 9 to about 12 millimeters thick to support the stress placed thereon.
- Referring back to FIGURE 5,
surface 42 is illustrated as a depressed area betweenshoulders - The final feature of
socket 30 ispin receptacle 58 which preferably includesbushing 60 therein.Pin receptacle 58 is located inbulb 62 ofsocket 30 but is offset from the center axis ofbulb 62. More specifically, and to minimize angular stress in the tension member,receptacle 58 is offset toward theload side 34 ofsocket 30 and is positioned to be aligned on center with a tension member assembled with said termination member, By so locating the receptacle, and thus the pivot point in the system, the load hanging therefrom is aligned with the load side of the tension member engaged with the termination device of the invention. -
Socket 30 is important to the functionality of the termination device of the invention principally because it provides three distinct friction zones and a smooth bend surface for the tension member. The combination reduces the compression force required to prevent tension member slippage which is particularly helpful where flexible flat tension members having polymeric jackets are employed. Reducing the compression force that would otherwise be required, alleviates creep and reduces stress in the tension member. This is desirable since it may reduce the number of re-roping operations that would be carried out during the life of the elevator. - Thus far only the
socket 30 has been described and it will be apparent to one of ordinary skill in the art that the socket alone does not retain the tension member. Reference is, therefore, made to FIGURES 7 and 8 where the load side and cutside plates plate 80 andplate 96 are identical in a preferred embodiment and are provided distinct numerals merely to distinguish each side of the termination device (which is side dependent) rather than to signify any distinction between the plates themselves. -
Plates end 82, reduce fatigue of the tension member at the point where it enters the termination device. The curve at 82 preferably mirrors thetapered end 32 ofsocket 30.Bottom end 84 is curved to match the transition from the compression portion ofsocket 30 tobulb 62. In a preferred embodiment, the curves at 82 and 84 as well as those in theopposite plate 96 are identical so thatplates - On the
convex side 86 of eachplate 80 and 96 (it should be noted that the sub numerals employed to describe features of each plate will be identical because the features are identical and no distinction as to side of the termination device is necessary), aregion 88 is provided where a textured surface is desirable. The texture may be of any type that increases the coefficient of friction without being significantly deleterious to the jacket of the tension member. In one preferred embodiment sand blasting of the region is indicated. It will be understood that the region may be textured by machining, chemical etching, knurling, etc. if desired or otherwise indicated. A preferred range of friction for the device of the invention is about .15 to about .5,Region 88 is outlined in FIGURE 8 in phantom lines. - Due to the texturing processes, and especially the sand blasting process, the termination device may become more susceptible to corrosion. In order to avoid or inhibit such corrosion, it has been determined that yellow zinc plating may be advantageously used. Alternatively, stainless steel material or aluminum material may be used for the device of the invention.
- Bordering
Region 88 on each longitudinal side thereof are a plurality of clearance holes 90. In a preferred embodiment, seven holes 90 are provided on each side ofRegion 88. Holes 90 accept through passage of bolts to assembledevice 10 and alsostuds 52 discussed with reference to FIGURE 6. Although it has been stated thatplates load side plate 80 which correspond tostuds 52 estimating only from thecut side 36 ofsocket 30. The holes that can be eliminated may be ascertained by reference to FIGURE 9 whereinbolts 100 are illustrated as extending through the entire assembly andstuds 52 only extend through one side thereof, therefore only requiring clearance holes 90 in the cut side plate. - Referring to FIGURES 9 and 10, the
device 10 is illustrated in the assembled condition withbolts 100 andstuds 52 properly torqued. The torque applied is discussed further hereunder but is dictated by the allowed pressure on the tension member which is about 2 Mpa on the load side and about 5 Mpa on the cut side of thetermination device 10. - Preferably a biasing arrangement is included in the assembly of
device 10, more specifically, it is desirable to anticipate possible creep of the tension member and therefore provide means to maintain the prescribed normal force on the tension member even if it is reduced in thickness by the effects of creep. One such arrangement is illustrated in FIGURES 11 and 12. In FIGURE 11, the biasing arrangement of a stack ofbelleville washers 102 is illustrated in the uncompressed state. FIGURE 12 on the other hand, illustrates the same stack ofwashers 102 after torquing of thebolt 100. In the event the volume of material bound between abolt head 194 and nut 106 (FIGURE 9) decreases after torquing, due to creep of the tension member,washers 102 will expand and maintain the pressure on the tension member. The normal pressure on the tension member will thus be maintained. The additional benefit of easy visual inspection for creep is realized by the invention since if the washers exhibit a spaced appearance like that of FIGURE 11, retorquing is required. Belleville washers are known to the art and do not require specific explanation. Other biasing means are also employable with the device of the invention with the joining concept being that the predetermined normal force on the tension member be maintained. One alternate biasing means is a corrugatedspring metal sheet 100 which would be placed atop cutside plate 96 in place ofwashers 102.Sheet 110 hasholes 112 for through passage ofbolts 100 orstuds 52 depending upon location.Holes 112 are preferably slotted to allow for longitudinal expansion of the spring sheet during torquing of fasteners and consequent compression ofspring sheet 110. - Referring now to FIGURE 14, a schematic view of the invention with the plates exploded from the socket and with the forces and tensions required indicated. The invention provides five friction areas which combine to form three friction zones. The areas include; (1) the inside surface of the load side plate which contacts one side of the tension member; (2) the load side of the socket (corresponds to load plate) providing friction on an opposite side of the tension member from the load side plate; (3) the bulbous section which provides a continuous frictional surface on which the tension member is on contact; (4) the cut side of the socket and (5) the cut side plate inside surface, surfaces 4 and 5 being opposed. These five areas create three friction zones that are resolved in the following equations to determine adequacy of the assembly. Each zone is mathematically quantifiable. The sum of the three frictions must be sufficient to prevent slippage. Practically speaking, it is desirable to attain a 100% holding efficiency. In order to achieve this efficiency, the sum of the three friction zones must be equal to or exceed the breaking strength of the tension member being employed. With an assembly having a 100% holding efficiency, the tension member will break before the termination device allows the tension member to slip. In the following equations, several assumptions are made: The rope breaking strength is 30,000 Newtons; the coefficient of friction (µ) for the sand blasted surfaces that are preferred in the invention is .25; and the plate normal force is a function of the number of bolts employed multiplied by 1540 Newtons which is the expected force delivered by each bolt. These numbers are exemplary and clearly can be adjusted depending upon circumstances. One of ordinary skill in the art following exposure to this disclosure should be fully capable of adjusting the calculations to conform to any specific parameters given without undue experimentation. FIGURE 14 is informative and used in connection with the following formulas employed to determine gripping strength of
device 10 and stress in various components. -
- T1→T2 (Region 1)
- T2-T3, (Region 2)
- and T3-T4 (Region 3)
- FOR EXAMPLE, ASSUME
-
- T1 = 30,000 N = tension member Breaking Strength
- µ = .25 = coefficient of friction
- N1 = Plate normal force
= 12,320 N (8 bolts x 154ON) - F1 = µ (N1) 2 plates
- F1 = .25 (12,320) 2 plates
- F1 = 6160N
-
- From Previous Calculations,
- T3 = 10,405 N
and T4 must be = < 0 (values greater than 0 indicate tension member slippage) Cut side plate has 14 fasteners x 1540N (thestuds 52 are available only to the cut side plate)
Assume N2 > N1 = 21,560 N, and then calculate for slippage - T4=T3-F2
- and F2 = µ (N2) 2 plates
- F2 = 25 (21,560) 2
- F2 = 10,780 N
-
- IF F2 ≥T3,
design is adequate, tension member will not slip - F2 > T3 ? (YES)
10,780N > 10,405N, so
design is adequate - 125 mm long
-
- In this example the pressure is beyond that taught in the invention
- Tension member plates are 190 mm long
-
- IN THIS EXAMPLE THE PRESSURE EXERTED ON THE TENSION MEMBER IS ACCEPTABLE FOR BOTH SIDES OF THE TERMINATION DEVICE. THUS, PLATES ARE LONG ENOUGH.
- LOAD PER BOLT
N1 = N2 = 11,000 N -
- M8 - 8 mm course thread Pitch = 1.25
-
-
- Referring to FIGURE 15, a clevis is illustrated.
Clevis 120 is seen connected to the termination assembly in FIGURE 2 (in exploded condition). The clevis is conventional and will be easily recognized by one of skill in the art. Theclevis 120 is employed to provide a pivot point near a terminal end of the loaded tension member to reduce vibratory fatigue therein.Clevis 120 is connected tosocket 30 bypin 122 extending throughreceptacle 58. - Referring now to FIGURES 16-18, an
optional device 130 for use with thetermination device 10 is illustrated. The purpose ofdevice 130 is to jam withtermination device 10 in the unlikely event of tension member slippage throughdevice 10.Device 130 is clamped onto the cut end of the tension member somewhere beyond region T4 as discussed above. When engaged with the tension member,device 130 cannot move thereon. Thus, if the tension member slipped it would drawdevice 130 into contact withcut side plate 96 andside 36 ofsocket 30 and would jam there preventing further slippage. -
Device 130 comprises a female portion 132 (FIGURE 17) and a male portion 150 (FIGURE 18).Female portion 132 features atension member groove 134 approximately the thickness of the tension member which is intersected bycrimp grooves fasteners 142.Male portion 150 provides tensionmember deformation ridges grooves device 138.Portion 150 further includesholes 156 which are coaxially withholes 140 whendevice 130 is assembled to facilitate through passage ofassembly bolts 142. - In use, a cut end of a tension member, i.e., the end not being used to support the elevator, is inserted in
groove 134 andportion 150 is placed in position. When thebolts 142 are tightened,ridges grooves device 130 and ifdevice 130 moves into contact withdevice 10 to tension member slippage, the slippage will be arrested. - A principal feature of the present invention is the flatness of the ropes used in the above described elevator system. The increase in aspect ratio results in a rope that has an engagement surface, defined by the width dimension "w", that is optimized to distribute the rope pressure. Therefore, the maximum rope pressure is minimized within the rope. In addition, by increasing the aspect ratio relative to a round rope, which has an aspect ratio equal to one, the thickness "t1"of the flat rope (see FIGURE 19) may be reduced while maintaining a constant cross-sectional area of the portions of the rope supporting the tension load in the rope.
- As shown in FIGURE 19 and 20, the flat ropes 722 include a plurality of individual load carrying cords 726 encased within a common layer of coating 728. The coating layer 728 separates the individual cords 726 and defines an engagement surface 730 for engaging the traction sheave 724. The load carrying cords 726 may be formed from a high-strength, lightweight non-metallic material, such as aramid fibers, or may be formed from a metallic material, such as thin, high-carbon steel fibers. It is desirable to maintain the thickness "d" of the cords 726 as small as possible in order to maximize the flexibility and minimize the stress in the cords 726. In addition, for cords formed from steel fibers, the fiber diameters should be less than .25 millimeters in diameter and preferably in the range of about.10 millimeters to .20 millimeters in diameter. Steel fibers having such diameter improve the flexibility of the cords and the rope. By incorporating cords having the weight, strength, durability and, in particular, the flexibility characteristics of such materials into the flat ropes, the traction sheave diameter "D" may be reduced while maintaining the maximum rope pressure within acceptable limits.
- The engagement surface 730 is in contact with a corresponding surface 750 of the traction sheave 724. The coating layer 728 is formed from a polyurethane material, preferably a thermoplastic urethane, that is extruded onto and through the plurality of cords 726 in such a manner that each of the individual cords 726 is restrained against longitudinal movement relative to the other cords 726. Other materials may also be used for the coating layer if they are sufficient to meet the required functions of the coating layer: traction, wear, transmission of traction loads to the cords and resistance to environmental factors. It should be understood that although other materials may be used for the coating layer, if they do not meet or exceed the mechanical properties of a thermoplastic urethane, then the benefits resulting from the use of flat ropes may be reduced. With the thermoplastic urethane mechanical properties the traction sheave 724 diameter is reducible to 100 millimeters or less.
- As a result of the configuration of the flat rope 722, the rope pressure may be distributed more uniformly throughout the rope 722. Because of the incorporation of a plurality of small cords 726 into the flat rope elastomer coating layer 728, the pressure on each cord 726 is significantly diminished over prior art ropes. Cord pressure is decreased at least as n-½, with n being the number of parallel cords in the flat rope, for a given load and wire cross section. Therefore, the maximum rope pressure in the flat rope is significantly reduced as compared to a conventionally roped elevator having a similar load carrying capacity. Furthermore, the effective rope diameter 'd' (measured in the bending direction) is reduced for the equivalent load bearing capacity and smaller values for the sheave diameter 'D' may be attained without a reduction in the D/d ratio. In addition, minimizing the diameter D of the sheave permits the use of less costly, more compact, high speed motors as the drive machine.
- A traction sheave 724 having a traction surface 750 configured to receive the flat rope 722 is also shown in FIGURE 19. The engagement surface 750 is complementarily shaped to provide traction and to guide the engagement between the flat ropes 722 and the sheave 724. The traction sheave 724 includes a pair of rims 744 disposed on opposite sides of the sheave 724 and one or more dividers 745 disposed between adjacent flat ropes. The traction sheave 724 also includes liners 742 received within the spaces between the rims 744 and dividers 745. The liners 742 define the engagement surface 750 such that there are lateral gaps 754 between the sides of the flat ropes 722 and the liners 742. The pair of rims 744 and dividers, in conjunction with the liners, perform the function of guiding the flat ropes 722 to prevent gross alignment problems in the event of slack rope conditions, etc. Although shown as including liners, it should be noted that a traction sheave without liners may be used.
- While preferred embodiments have been shown and described, various modifications and substitutions may be made thereto without departing from the spirit and scope of the invention. Accordingly, it is to be understood that the present invention has been described by way of illustration and not limitation.
and T4=O ,
since if T4>O tension member will slip in the termination device
so T2 = (30,000-6160)=
= 23,840N
Claims (20)
- A tension member termination device (10) comprising:a tension member compressor having at least one area that will contact a tension member having a traction enhanced surface thereon.
- A tension member termination device (10) for an elevator system comprising:a socket (30) having a bulbous end, said socket defining a tension member path therearound;a load side plate (80) affixable to said socket (30) to apply a normal pressure to a load side of an end of a tension member between said socket (30) and said load side plate (80);a cut side plate (96) affixable to said socket (30) to apply a normal pressure to a cut side of said end of said tension member between said socket (30) and said cut side plate (96).
- A tension member termination device for an elevator system as claimed in claim 2 wherein said path defined by said socket includes a surface which is textured to increase the coefficient of friction thereof
- A tension member termination device for an elevator system as claimed in claim 3 wherein said surface is sand blasted.
- A tension member termination device for an elevator system as claimed in claim 2, 3 or 5 wherein said load side plate (80) and said cut side plate (96) are affixed to said socket (30) by a plurality of fasteners (100) common to both plates.
- A tension member termination device for an elevator system as claimed in any of claims 2 to 5 wherein said socket (30) further includes studs (52) extending from said socket (30) in a direction to intersect said cut side plate (96) enabling a greater compressive load to be placed upon said cut side plate (96) than said load side plate (80).
- An elevator system having an elevator car (14), a machine (20) a counterweight (16) and a flexible flat tension member (22) extending between said counterweight (16) and said elevator car (14), said tension member being terminated to at least one of said car and said counterweight by a termination device (10) comprising:a socket (30) having a relatively narrow section and a relatively bulbous section (62), said socket defining a tension member pathway therearound and a fastener section for through passage of fasteners (100);a load side plate (80) fastenable to said socket (30) by said fasteners (100), said load side plate (80) extending along said relatively narrow section of said socket on a load side thereof;a cut side plate (96) fastenable to said socket (30) by said fasteners (100), said cut side plate (86) extending along said relatively narrow section of said socket (30) on a cut side thereof.
- An elevator system as claimed in claim 7 wherein said flexible flat tension member (22) is located between said load side plate (80) and said socket (30), extends around said bulbous section in contact therewith and between said cut side plate (96) and said socket (30).
- An elevator system as claimed in claim 7 or 8 wherein said socket (30) further includes studs (52) extending from said relatively narrow section and toward said cut side plate (96) to provide additional compressive capability to said cut side plate (96).
- An elevator system as claimed in claim 9 wherein said load side plate (96) compresses said tension member (22) to about 2 MPa.
- An elevator system as claimed in claim 10 wherein said cut side plate (96) compresses said tension member (22) to about 5 MPa.
- An elevator system as claimed in any of claims 7 to I 1 wherein said socket (30) and said load side plate (80) and said cut side plate (96) all include a textured surface corresponding to surfaces contacted by said tension member (22).
- An elevator system as claimed in claim 12 wherein said surfaces are sand blasted.
- An elevator system as claimed in any of claims 7 to 13 wherein said socket (30) further includes a pivot pin receiver (58) in said bulbous section (62).
- An elevator system as claimed in claim 14 wherein said receiver (58) is located in said bulbous section (62) so as to be aligned with a load side of said tension member (22) when engaged by said termination device.
- A termination device (10) for a tension member (22) comprising:a compressive system to engage and compress a tension member (22);a biaser (102;110) to maintain a selected compressive force on said tension member (22).
- A spring loaded clamp for termination of a tension member (10) comprising:a clamp having at least two members;a plurality of fasteners (100) to fasten said members together in compressive relationship;at least one biaser (102;110) arranged to maintain said compressive relationship.
- A method for terminating a tension member comprising:feeding said tension member into a first side of a compressive system in one direction and looping said tension member back through a second side of said compressive system;spring loading said compressive system;compressing said compressive system around said tension member whereby said spring loading maintains a set compressive load on said tension member.
- A method according to claim 18 wherein said compressing comprises compressing said first side of said compressive system to a first force and compressing said second side of said compressive system to a second force,
- A method according to claim 19 wherein said second force is higher than said first force.
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US09/031,108 US6401871B2 (en) | 1998-02-26 | 1998-02-26 | Tension member for an elevator |
US09/218,989 US6820726B1 (en) | 1998-12-22 | 1998-12-22 | Traction enhanced controlled pressure flexible flat tension member termination device |
US09/218,990 US6739433B1 (en) | 1998-02-26 | 1998-12-22 | Tension member for an elevator |
EP99907157A EP1028911B1 (en) | 1998-02-26 | 1999-02-19 | Flat cable connecting device |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP99907157A Division EP1028911B1 (en) | 1998-02-26 | 1999-02-19 | Flat cable connecting device |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1710194A2 true EP1710194A2 (en) | 2006-10-11 |
EP1710194A3 EP1710194A3 (en) | 2008-11-26 |
EP1710194B1 EP1710194B1 (en) | 2014-03-26 |
Family
ID=42676770
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP06014420.1A Expired - Lifetime EP1710194B1 (en) | 1998-02-26 | 1999-02-19 | Cable connecting device |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP1710194B1 (en) |
ES (1) | ES2458565T3 (en) |
PT (1) | PT1028911E (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2910509A1 (en) * | 2014-02-19 | 2015-08-26 | KONE Corporation | Rope clamp for an elevator. |
CN115012237A (en) * | 2022-06-01 | 2022-09-06 | 西安特种设备检验检测院 | Fatigue-resistant elevator steel wire rope |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DD115089A5 (en) * | 1974-12-02 | 1975-09-12 | ||
DE2915241A1 (en) * | 1979-04-14 | 1980-10-23 | Rudolf Dr Ing Vogel | Load handling installation e.g. for hoisting - uses steel bands to carry load passed around driven roller with surrounding ring compensating for offset |
JP3412270B2 (en) * | 1994-07-27 | 2003-06-03 | 株式会社ダイフク | Detecting device for slack of suspension belt of lifting device |
-
1999
- 1999-02-19 PT PT99907157T patent/PT1028911E/en unknown
- 1999-02-19 EP EP06014420.1A patent/EP1710194B1/en not_active Expired - Lifetime
- 1999-02-19 ES ES06014420T patent/ES2458565T3/en not_active Expired - Lifetime
Non-Patent Citations (1)
Title |
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None |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2910509A1 (en) * | 2014-02-19 | 2015-08-26 | KONE Corporation | Rope clamp for an elevator. |
US9902595B2 (en) | 2014-02-19 | 2018-02-27 | Kone Corporation | Elevator |
CN115012237A (en) * | 2022-06-01 | 2022-09-06 | 西安特种设备检验检测院 | Fatigue-resistant elevator steel wire rope |
CN115012237B (en) * | 2022-06-01 | 2023-11-10 | 西安特种设备检验检测院 | Fatigue-resistant elevator steel wire rope |
Also Published As
Publication number | Publication date |
---|---|
EP1710194A3 (en) | 2008-11-26 |
ES2458565T3 (en) | 2014-05-06 |
EP1710194B1 (en) | 2014-03-26 |
PT1028911E (en) | 2007-01-31 |
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