Rope, elevator arrangement and elevator

Abstract

The invention relates to a belt-shaped rope of an elevator having opposite lateral sides facing in thickness direction of the rope, at least one of the lateral sides being shaped to have elongated wedge-shaped ribs that are disposed adjacent each other in width direction of the rope and extend parallel with the longitudinal direction of the rope, each said wedge-shaped rib having a first flank face and a second flank face that are at an acute angle relative to each other, and the surface material of said flank faces has shore A hardness more than 85 and less than 100. The invention also relates to an elevator arrangement as well as to an elevator, implementing the aforementioned belt-shaped rope.

Claims

1. A belt-shaped rope of an elevator, the belt-shaped rope comprising: one or more load bearing members extending parallel with a longitudinal direction of the rope; and a coating forming a surface of the rope with the one or more load bearing members embedded therein and opposite lateral sides of the surface of the rope facing each other in a thickness direction of the rope, at least one of the lateral sides being shaped to have elongated wedge-shaped ribs that are disposed adjacent each other in a width direction of the rope and extend parallel with the longitudinal direction of the rope, each said wedge-shaped rib having a first flank face and a second flank face that are at an acute angle relative to each other that is greater than 45 degrees and less than 60 degrees, and a material of the surface of the coating at said flank faces has a shore A hardness more than 90 and less than 100.

2. The belt-shaped rope according to claim 1, wherein said hardness is from 91 to 94 shore A.

3. The belt-shaped rope according to claim 1, wherein said acute angle is from 52 to 58 degrees.

4. The belt-shaped rope according to claim 1, wherein said acute angle is from 52 to 58 degrees, and said hardness is from 91 to 94 shore A.

5. The belt-shaped rope according to claim 1, wherein said material comprises polymer.

6. The belt-shaped rope according to claim 1, wherein said at least one of the lateral sides is shaped to have one or more elongated grooves, each extending between neighboring ribs parallel with the longitudinal direction of the rope and each said groove is delimited by flank faces of neighboring ribs that are at an acute angle relative to each other.

7. The belt-shaped rope according to claim 1, wherein each said flank face of the belt-shaped rope is planar.

8. The belt-shaped rope according to claim 7, wherein a height of each said planar flank face of the belt-shaped rope is more than half of a height of the rib, as measured in the thickness direction of the rope.

9. The belt-shaped rope according to claim 1, wherein each said flank face of the belt-shaped rope is a flank face for contacting a flank face of a rib of a rope wheel.

10. The belt-shaped rope according to claim 1, wherein the one or more load bearing members extend parallel with the longitudinal direction of the rope unbroken throughout the rope.

11. The belt-shaped rope according to claim 1, wherein said load bearing members are made of composite material including reinforcing fibers embedded in polymer matrix, said reinforcing fibers being carbon fibers or glass fibers.

12. The belt-shaped rope according to claim 11, wherein the module of elasticity E of the polymer matrix is over 2 GPa.

13. The belt-shaped rope according to claim 1, wherein both of the lateral sides of the rope are shaped to have elongated wedge-shaped ribs that are disposed adjacent each other in width direction of the rope and extend parallel with the longitudinal direction of the rope, each said wedge-shaped rib having a first flank face and a second flank face that are at an acute angle relative to each other, and the material of the surface of the coating at said flank faces has shore A hardness more than 90 and less than 100.

14. An elevator arrangement comprising: the belt-shaped rope of claim 1; and at least one rope wheel provided with a counterpart shape for the rope, and said at least one belt-shaped rope is arranged to pass around said at least one rope wheel.

15. The elevator arrangement according to claim 14, wherein the rope wheel comprises: elongated wedge-shaped grooves that are disposed adjacent each other in axial direction of the rope wheel and extend along the circumference of the rope wheel parallel with each other, and the ribs of the rope extend into grooves of the rope wheel.

16. The elevator arrangement according to claim 14, wherein said rope is a suspension rope arranged to suspend an elevator car.

17. The elevator arrangement according to claim 14, wherein said at least one rope wheel comprises: two rope wheels, which are each provided with a counterpart shape for the rope, and said at least one belt-shaped rope is arranged to pass around each of said two rope wheels such that a lateral side of the rope shaped to have elongated wedge-shaped ribs engages a counterpart shape of the rope wheel in question.

18. The elevator arrangement according to claim 17, wherein said two rope wheels have mutually nonparallel horizontal rotational axes.

19. The elevator arrangement according to claim 18 wherein said two rope wheels have mutually nonparallel rotational axes, which are at an angle 30-90 degrees.

20. The elevator arrangement according to claim 14, wherein said at least one rope wheel comprises: two rope wheels, which are provided with a counterpart shape for the rope, and said at least one belt-shaped rope is arranged to pass around said two rope wheels such that one its lateral sides shaped to have elongated wedge-shaped ribs engages the counterpart shape of one of the rope wheels, and the other of its lateral sides shaped to have elongated wedge-shaped ribs engages the counterpart shape of the other of the rope wheels.

21. An elevator comprising: the elevator arrangement according to claim 14; and an elevator car connected to the belt-shaped rope.

22. The belt-shaped rope according to claim 1, wherein tips of the elongated wedge-shaped ribs are rounded in the width direction of the rope.

23. The belt-shaped rope according to claim 22, wherein, when the belt-shaped rope engages with a rope wheel, air gaps are formed between the tips of the elongated wedge-shaped ribs and the rope wheel.

24. The belt-shaped rope according to claim 1, wherein the one or more load bearing members are substantially rectangular and larger in the width direction than the thickness direction of the rope.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) In the following, the present invention will be described in more detail by way of example and with reference to the attached drawings, in which

(2) FIG. 1 illustrates a cross-sectional view of a first embodiment of a rope.

(3) FIG. 2 illustrates a cross-sectional view of a second embodiment of a rope.

(4) FIG. 3a illustrates a first embodiment of an elevator arrangement implementing rope of FIG. 1 or FIG. 2.

(5) FIG. 3b illustrates a second embodiment of an elevator arrangement implementing rope of FIG. 1 or FIG. 2.

(6) FIG. 4 illustrates a preferred cross-sectional view of a rope wheel of the elevator arrangement.

(7) FIG. 5 illustrates the rope of FIG. 1 and a rope wheel of FIG. 4 engaging each other.

(8) FIG. 6 illustrates the rope of FIG. 2 and the rope wheel of FIG. 4 engaging each other.

(9) FIGS. 7 and 8 illustrate preferred details of a load bearing member of the rope.

(10) FIG. 9 illustrates a pulley arrangement where rope twist is present.

(11) FIG. 10 illustrates a first embodiment of an elevator implementing a rope and an elevator arrangement.

(12) FIG. 11 illustrates a second embodiment of an elevator implementing a rope and an elevator arrangement.

(13) The foregoing aspects, features and advantages of the invention will be apparent from the drawings and the detailed description related thereto.

DETAILED DESCRIPTION

(14) FIGS. 1 and 2 each illustrate a preferred embodiment of a belt-shaped rope 1,1′ of an elevator having two opposite wide lateral sides S1, S2, i.e. lateral sides that extend in width direction of the rope 1,1′ and face in thickness direction t of the rope 1,1′.

(15) In the embodiment of FIG. 1, one of the lateral sides S1, S2, is shaped to have elongated wedge-shaped ribs 2 that are disposed adjacent each other in width direction w of the rope 1 and extend parallel with the longitudinal direction 1 of the rope 1. This embodiment suits well to be used in elevator arrangements where ribs are needed on one side of the rope 1. This is the case for instance in elevators where only one side of the rope 1 comes in contact with the rope wheels of the elevator when running along its route. In the embodiment of FIG. 2, each of the two lateral sides S1, S2 is shaped to have elongated wedge-shaped ribs 2 that are disposed adjacent each other in width direction w of the rope 1′ and extend parallel with the longitudinal direction 1 of the rope 1′. This embodiment suits well to be used in elevator arrangements where ribs are needed on two opposite sides of the rope 1′. This is the case for instance in elevators where two opposite sides of the rope 1′ come in contact with the rope wheels of the elevator when running along its route.

(16) In the embodiments of FIGS. 1 and 2, each said side S1;S1,S2 that is shaped to have elongated wedge-shaped ribs 2 is also shaped to have one or more elongated wedge-shaped grooves 3, each extending between neighboring ribs 2 parallel with the longitudinal direction 1 of the rope 1,1′ and each said groove 3 is delimited by flank faces 2a, 2b of neighboring ribs 2 that are at an acute angle (alfa) relative to each other. The number of the grooves depends on how many ribs 2 the rope is designed to comprise. Each said wedge-shaped rib 2 has a first flank face 2a and a second flank face 2b. The surface material of the rope 1,1′ forming said flank faces 2a, 2b has shore A hardness more than 85, more preferably hardness 90 or more, however less than 100. The first flank face 2a and a second flank face 2b are at an acute angle (alfa) relative to each other. The material being relatively hard and the flank angle being sharp provides that the bandwidth of the friction can be maintained stable throughout the life time of the rope yet maintaining good capacity to achieve traction. It has been noticed that with the hard material, variation of the traction conditions between the rope 1,1′ and a rope wheel can maintained low. Due to relatively hard material, the friction coefficient of the surface becomes moderate or at least relatively low, which on the other hand is eliminated by the acute angle design for increasing the groove factor. Groove factor indicates the ability of a groove of a rib of a rope wheel to produce normal force and surface pressure on the flank face of the rib of a rope. The combination of hard surface material, and acute flank angle furthermore facilitate stability of the rope system by reducing random occurrence of climbing of the rope 1,1′ along either of the flank faces of the groove of the rope wheel wherein the rope is fitted during use, which makes the rope 1,1′ more stable as the system becomes more tolerant of twist or fleet angle, regardless of whether it is unintended or designed in the system on purpose. The solution thus suits very well for an elevator where twist and/or fleet angle is/are likely to occur.

(17) The flank faces 2a, 2b form the opposite side faces of the rib 2, each facing obliquely in width direction w of the rope 1,1′. The ribs 2 and grooves 3 of the rope 1,1′ are suitable for interacting with ribs and grooves of rope wheels around which the rope 1,1′ is arranged to pass. The interaction is intended for producing lateral guidance for the rope 1,1′ and/or for increasing frictional contact area between the rope 1,1′ and a rope wheel. Therefore, the ribs 2 of the rope 1,1′ are ribs suitable for extending into grooves of a rope wheel, wherein the rope wheel is a rope wheel provided with counterpart shape for the rope 1,1′ and comprising elongated wedge-shaped grooves that are disposed adjacent each other in axial direction x of the rope wheel and extend along the circumference of the rope wheel parallel with each other. The grooves 3 of the rope 1,1′, on the other hand, are grooves suitable for receiving ribs of said rope wheel.

(18) Said surface material preferably comprises polymer. Preferably more than 80% of it is of polymer (weight proportion). Preferably, said polymer is polyurethane, such as thermoplastic polyurethane. As a further alternative, said polymer can be rubber or silicone. Also other alternative polymer materials can be used.

(19) In the following, preferred further details of the rope 1,1′ are described. In the preferred embodiment, each said flank face 2a,2b is planar. In FIGS. 1 and 2 each illustrating a cross sections of a rope 1,1′, this is visible as the outlines of the flank faces 2a,2b are straight. The cross section of the rope 1,1′ continues the same in its longitudinal direction 1 at least to the amount that the outlines of the flank faces 2a,2b continues the same in longitudinal direction 1 of the rope 1,1′. It is further preferred, that the height h.sub.1 of each said planar flank face 2a,2b is more than half of the height h.sub.2 of the rib 2, as measured in thickness direction of the rope 1,1′. In this way, a vast contact area between the planar flank face and flank face of a rib of a rope wheel 4 can be produced.

(20) As for the more specific shape of the wedge-shaped ribs 2, it is preferable that each said rib is V-shaped as viewed in longitudinal direction of the rope 1, preferably with a rounded tip, as illustrated in FIG. 1. As for the more specific shape of the wedge-shaped grooves 3 it is likewise preferable that each said groove is V-shaped as viewed in longitudinal direction of the rope 1,1′, preferably with a rounded bottom. The rounded bottom provides that the groove 3 is less prone to formation of cracks, which is advantageous particularly due to the hardness being relatively high, and the ability of the material to even out internal tension thereby being more limited.

(21) As mentioned, said shore A hardness values are high at least to the extent that the hardness is more than 85. The advantageous effect on maintainability of the bandwidth of the friction factor stable throughout the life time of the rope starts to appear when the hardness is more than 85. The effect becomes gradually more substantial, and when said hardness value is as high as 90 Shore A or more the advantageous effects appear strongly. At its optimum, said hardness is from 91 to 94 shore A, most preferably 92 shore A. Generally, this narrow subrange provides good results with regard to maintainability of the bandwidth of the friction factor stable yet good capacity to achieve traction can still be easily obtained and the negative effects of the relatively hard material are still moderate and possible to eliminate with the acute angle. Other negative effects start to gradually appear when the hardness becomes very high, such as an excessively large turning radius and sensitivity to cracking. Due to this, it is in general preferable that said hardness is less than 100 shore A.

(22) As for the acute angle alfa, it is preferable that the angle is substantially less than 90 degrees, such as less than 80 degrees. The sharper the angle alfa is, the better it can eliminate challenges induced by hard surface material. The increase in groove factor starts to show first with low gradient, and increases strongly when said acute angle is in the range below 60 degrees. The harder the surface material is, the sharper the angle alfa should be when aiming to optimum. Accordingly, with high shore A hardness values, and particularly when said hardness value is as high as 90 Shore A or more, it is preferable that said acute angle is less than 60 degrees. The optimal range of said acute angle is noticed to be with high shore A hardness values, and particularly when said hardness value is as high as 90 Shore A or more, from 52 to 58 degrees.

(23) Other negative effects start to gradually appear when the angle alfa is very small. The friction and surface pressure on the rope are likely to become excessively high and lead to problems relating to strength of the rope surface and general frictional interaction between the elevator rope and the rope wheel. For this reason, it is generally preferable that said acute angle is more than 45 degrees, particularly preferably more than 50 degrees.

(24) Generally, best results with regard to maintainability of the bandwidth of the friction factor stable yet maintaining good capacity to achieve traction were obtained with said high hardness being from 91 to 94 shore A and the angle alfa being from 52 to 58 degrees. Best results were obtained with the specific angle alfa being 54 degrees and said Shore A hardness being 92.

(25) The structure of the rope 1,1′, in general, is preferably such that the cross section of the rope 1,1′ continues the same in its longitudinal direction 1 at least to the amount that the ribs 2 and the grooves 3 are continuous. Thereby, they extend continuously the whole length of the rope 1,1′. Thereby, they can serve their purpose, e.g. produce lateral guidance for the rope and/or increase frictional contact area between the rope and the rope wheel, throughout the length of the rope 1,1′, fitting and interacting with the counterpart shape of the rope wheel without difficulties.

(26) The rope 1,1′ can be implemented in various different elevator arrangements. FIGS. 3a and 3b illustrate each an elevator arrangement comprising and implementing a belt-shaped rope 1,1′, which is as described with reference to FIG. 1 or 2, and at least one rope wheel 4 provided with counterpart shape for the rope 1,1′, in particular for a lateral side S1,S2 thereof that is shaped to have elongated wedge-shaped ribs 2 as described above. The belt-shaped rope 1,1′ is arranged to pass around said at least one rope wheel 4 such that a lateral side of the rope shaped to have elongated wedge-shaped ribs engages the counterpart shape of the rope wheel 4. The rope wheel 4 can be a freely rotating rope wheel or a drive wheel rotatable with a motor. FIGS. 3a and 3b illustrate also further rope wheels 40,41, each of which can correspondingly be provided with counterpart shape for the rope 1,1′.

(27) FIG. 4 illustrates preferred details of the aforementioned rope wheel 4,40,41. The rope wheel 4,40,41 is more specifically such that it comprises elongated wedge-shaped grooves 5 that are disposed adjacent each other in axial direction x of the rope wheel 4,40,41, i.e. in direction of the rotational axis thereof, and extend along the circumference of the rope wheel 4,40,41 parallel with each other.

(28) FIG. 5 illustrates the rope 1 of FIG. 1 and a rope wheel 4,40,41 of FIG. 4 engaging each other. FIG. 6 illustrates the rope 1′ of FIG. 2 and the rope wheel 4,40 of FIG. 4 engaging each other. As illustrated in FIGS. 5 and 6, the ribs 2 of the rope 1 extend into grooves 5 of the rope wheel 4,40,41. The rope wheel 4,40,41 comprises elongated wedge-shaped ribs 6 that are disposed adjacent each other in axial direction x of the rope wheel 4 and extend along the circumference of the rope wheel 4,40,41 parallel with each other, each said groove 5 being delimited by flank faces 6a, 6b of neighboring ribs 6 that are at an acute angle alfa relative to each other. It is preferable, correspondingly as above explained for the rope structure, that each said flank face 6a,6b are planar. In FIG. 4 illustrating a cross section of the rope wheel 4,40,41, this is visible as the outlines of the flank faces 6a,6b are straight. It is further preferred, that the height of each said planar flank face 6a,6b is more than half of the height of the rib 6, as measured in radial direction of the rope wheel 4, i.e. in the direction corresponding thickness direction of the rope 1,1′.

(29) In the preferred embodiments illustrated in FIGS. 5 and 6, tips of the ribs 6 of the rope wheel 4,40,41 can be shaped either flat, as illustrated, or alternatively, rounded (not illustrated), such that an air gap g is formed between the tips and the bottom of the groove 3 of the belt-shaped rope 1,1′ when the belt-shaped rope 1,1′ and the rope wheel 4,40,41 are engaged. The air gap g provides that the splitting forces and the deformation at the groove bottom structures are evened out within a bigger material amount and sensitivity to cracks is decreased, which is advantageous particularly due to the hardness being relatively high, and the ability of the material to yield and even out internal tension thereby being more limited. The gaps g also can receive dirt such that the dirt does not wedge between the groove bottom and the rib tip. The rib tips of the rope wheel being flat, it is meant that the cross section of the rib tip is flat. The outline of the cross section of the flat rib tip extends straight in axial direction of the rope wheel 4,40,41. The advantage of a flat rib top is that the rope wheel is simple to manufacture and an air gap g can be simply ensured. The height of said air gap g between the tips of the ribs 6 and the bottom of the groove 3 of the belt-shaped rope 1,1′ is at least 0.2 mm or more, as measured in thickness direction of the belt-shaped rope 1,1′.

(30) In the preferred embodiments illustrated in FIGS. 5 and 6, the tips of the ribs 2 of the belt-shaped rope 1,1′ are rounded such that an air gap g is formed between tips and the bottom of the groove 5 of the rope wheel 4,40,41 when the belt-shaped rope 1,1′ and the rope wheel 4,40,41 are engaged.

(31) FIGS. 1 and 2 also illustrate preferred details for the internal structure of the rope 1,1′. The rope 1,1′ is preferably such that it comprises one or more load bearing members 10, and a coating 11 made of said surface material and forming the surface of the rope 1,1′, and the one or more load bearing members 10 are embedded in the coating 11 and extend unbroken throughout the length of the rope 1,1′ embedded in the coating 11. In this way, the optimal and accurate hardness of the surface material can be simply obtained without compromises with the load bearing function. If there are plurality of the load bearing members 10, they are preferably adjacent each other in width direction w of the rope 1,1′, as illustrated. As mentioned, said surface material preferably comprises polymer, preferably more than 80% of it being of polymer (weight proportion). Accordingly, the coating 11 comprises polymer correspondingly.

(32) Preferred details of the load bearing member(s) 10 of the rope 1,1′ are further described hereinafter referring to FIGS. 7 and 8. The rope 1,1′ being belt-shaped provides that it is turned around the rope wheels of the elevator around an axis extending in width direction w of the rope 1,1′. The width/thickness ratio of the rope 1,1′ is preferably at least 2 more preferably at least 4, or even more. In this way a large cross-sectional area for the rope 1,1′ is achieved, while the bending capacity around the width-directional axis is still feasible also with rigid materials of the load bearing member(s) 10, such as composite materials described later. Thereby, the rope 1,1′ suits very well to be used in hoisting appliances, in particular in elevators, wherein the rope 1,1′ needs to be guided to pass around one or more rope wheels with high speed. Also, it is preferable that the load bearing members 10 are wide. Accordingly, each of said one or more load bearing members 10 is preferably larger in width direction w of the rope than in thickness direction t of the rope 1,1′. Particularly, the width/thickness ratio of each of said one or more load bearing members is preferably more than 2. Thereby, the bending resistance of the rope 1,1′ is small but the load bearing total cross sectional area is vast with minimal non-bearing areas.

(33) FIG. 7 illustrates a preferred inner structure for said load bearing member 10, showing inside the circle an enlarged view of the cross section of the load bearing member 10 close to the surface thereof, as viewed in the longitudinal direction l of the load bearing member 10. The parts of the load bearing member 10 not showed in FIG. 7 have a similar structure. FIG. 8 illustrates the load bearing member 10 three dimensionally. The load bearing member 10 is made of composite material comprising reinforcing fibers f embedded in polymer matrix m. The reinforcing fibers f being in the polymer matrix means here that the individual reinforcing fibers f are bound to each other with a polymer matrix m. This has been done e.g. in the manufacturing phase by immersing them together in the fluid material of the polymer matrix which is thereafter solidified. The reinforcing fibers f are distributed substantially evenly in polymer matrix m and bound to each other by the polymer matrix m. The load bearing member 10 formed is a solid elongated rod-like one-piece structure. Said reinforcing fibers f are most preferably carbon fibers, but alternatively they can be glass fibers, or possibly some other fibers. Preferably, substantially all the reinforcing fibers f of each load bearing member 10 are parallel with the longitudinal direction of the load bearing member 10. Thereby, the fibers f are also parallel with the longitudinal direction of the rope 1,1′ as each load bearing member 10 are to be oriented parallel with the longitudinal direction of the rope 1,1′. This is advantageous for the rigidity as well as behavior in bending. Owing to the parallel structure, the fibers in the rope 1,1′ will be aligned with the force when the rope 1,1′ is pulled, which ensures that the structure provides high tensile stiffness. The fibers f used in the preferred embodiments are accordingly substantially untwisted in relation to each other, which provides them said orientation parallel with the longitudinal direction of the rope 1,1′. This is in contrast to the conventionally twisted elevator ropes, where the wires or fibers are strongly twisted and have normally a twisting angle from 15 up to 40 degrees, the fiber/wire bundles of these conventionally twisted elevator ropes thereby having the potential for transforming towards a straighter configuration under tension, which provides these ropes a high elongation under tension as well as leads to an unintegral structure. The reinforcing fibers f are preferably long continuous fibers in the longitudinal direction of the load bearing member 10, preferably continuing for the whole length of the load bearing member 10.

(34) As mentioned, the reinforcing fibers f are preferably distributed in the polymer matrix of the load bearing member 10 substantially evenly. The fibers f are then arranged so that the load bearing member 10 would be as homogeneous as possible in the transverse direction thereof. An advantage of the structure presented is that the matrix m surrounding the reinforcing fibers f keeps the interpositioning of the reinforcing fibers f substantially unchanged. It equalizes with its slight elasticity the distribution of force exerted on the fibers, reduces fiber-fiber contacts and internal wear of the rope, thus improving the service life of the rope 1,1′. Owing to the even distribution, the fiber density in the cross-section of the load bearing member 10 is substantially constant. The composite matrix m, into which the individual fibers f are distributed, is most preferably made of epoxy, which has good adhesiveness to the reinforcement fibers f and which is known to behave advantageously with reinforcing fibers such as carbon fiber particularly. Alternatively, e.g. polyester or vinyl ester can be used, but also any other suitable alternative materials can be used.

(35) The matrix m has been applied on the fibers f such that a chemical bond exists between each individual reinforcing fiber f and the matrix m. Thereby a uniform structure is achieved. To improve the chemical adhesion of the reinforcing fiber to the matrix m, in particular to strengthen the chemical bond between the reinforcing fiber f and the matrix m, each fiber can have a thin coating, e.g. a primer (not presented) on the actual fiber structure between the reinforcing fiber structure and the polymer matrix m. However, this kind of thin coating is not necessary. The properties of the polymer matrix m can also be optimized as it is common in polymer technology. For example, the matrix m can comprise a base polymer material (e.g. epoxy) as well as additives, which fine-tune the properties of the base polymer such that the properties of the matrix are optimized. The polymer matrix m is preferably of a hard non-elastomer, such as said epoxy, as in this case a risk of buckling can be reduced for instance. However, the polymer matrix need not be non-elastomer necessarily, e.g. if the downsides of this kind of material are deemed acceptable or irrelevant for the intended use. In that case, the polymer matrix m can be made of elastomer material such as polyurethane or rubber for instance.

(36) The reinforcing fibers f together with the matrix m form a uniform load bearing member, inside which no substantial abrasive relative movement occurs when the rope is bent. The individual reinforcing fibers f of the load bearing member 10 are mainly surrounded with polymer matrix m, but random fiber-fiber contacts can occur because controlling the position of the fibers in relation to each other in their simultaneous impregnation with polymer is difficult, and on the other hand, elimination of random fiber-fiber contacts is not necessary from the viewpoint of the functioning of the solution. If, however, it is desired to reduce their random occurrence, the individual reinforcing fibers f can be pre-coated with material of the matrix m such that a coating of polymer material of said matrix is around each of them already before they are brought and bound together with the matrix material, e.g. before they are immersed in the fluid matrix material.

(37) As above mentioned, the matrix m of the load bearing member 10 is most preferably hard in its material properties. A hard matrix m helps to support the reinforcing fibers f, especially when the rope bends, preventing buckling of the reinforcing fibers f of the bent rope, because the hard material supports the fibers f efficiently. To reduce the buckling and to facilitate a small bending radius of the load bearing member 10, among other things, it is therefore preferred that the polymer matrix m is hard, and in particular non-elastomeric. The most preferred materials for the matrix are epoxy resin, polyester, phenolic plastic or vinyl ester. The polymer matrix m is preferably such that its module of elasticity (E) is over 2 GPa, more preferably over 2.5 GPa, and less than 10 GPa. Most preferably the module of elasticity E is in the range 2.5-4.5 GPa. There are commercially available various material alternatives for the matrix m which can provide these material properties and means to adjust the values to be as desired. Preferably over 50% proportion of the surface area of the cross-section of the load bearing member 10 is of the aforementioned reinforcing fiber, preferably such that 50%-80% proportion is of the aforementioned reinforcing fiber, more preferably such that 55%-70% proportion is of the aforementioned reinforcing fiber, and substantially all the remaining surface area is of polymer matrix m. Most preferably, this is carried out such that approx. 60% of the surface area is of reinforcing fiber and approx. 40% is of matrix material (preferably epoxy material). In this way a good longitudinal stiffness for the load bearing member 10 is achieved. As mentioned carbon fiber is the most preferred fiber to be used as said reinforcing fiber due to its excellent properties in hoisting appliances, particularly in elevators. However, this is not necessary as alternative fibers could be used, such as glass fiber, which has been found to be suitable for the hoisting ropes as well. The load bearing member 10 is preferably completely non-metallic, i.e. made not to comprise metal.

(38) Hardness of the matrix m and/or orientation of the fibers f parallel with the longitudinal direction of the rope 1,1′ and/or the particular fiber selection (carbon) all have an increasing effect on the rigidity of the load bearing member 10 against bending. Owing to high rigidity resulting from the composite material, harder surface material than in prior solutions, is well compatible with it. The rope 1,1′, when it is rigid, particularly due to being made of composite material containing one or more of said features prone to increase rigidity against bending, is to be guided with rope wheels 4 of relatively large radius. Large radius benefits both the load bearing members 10 and the surface material as the hard surface material is prone to being sensitive to problems caused by surface material rigidity against bending. Accordingly, rigid load bearing members 10 are particularly advantageous in combination with the surface material having hardness 90 shore A or more. The diameter of the rope wheel 4 with composite material and hard surface material of the rope 1,1′ is preferably more than 250 mm.

(39) The rope 1,1′ is furthermore preferably such that the aforementioned load bearing member 10 or a plurality of load bearing members 10, comprised in the rope 1,1′, together cover majority, preferably 70% or over, more preferably 75% or over, most preferably 80% or over, most preferably 85% or over, of the width of the cross-section of the rope 1,1′ for essentially the whole length of the rope 1,1′. Thus, the supporting capacity of the rope 1,1′ with respect to its total lateral dimensions is good, and the rope 1,1′ does not need to be formed to be thick.

(40) FIG. 9 illustrates the elevator arrangement where fleet angle and rope twist exist in the rope configuration. As mentioned, the combination of hard surface material and sharp flank angle facilitate stability of this kind of rope system by reducing random occurrence of climbing of the rope 1,1′ along either of the flank faces of the groove of the rope wheel 4,40,41 wherein the rope is fitted during use. Relatively low friction coefficient resulting from the hard material and the sharp angle together reduce ability and likelihood of the rope to climb along the flank face and such that it can escapes the groove of the rope wheel 4,40,41. As a result, the behavior of the rope 1,1′ is more stable as the system becomes more tolerant of twist or fleet angle existing in the system intentionally or unintentionally.

(41) FIG. 10 illustrates an elevator comprising an elevator arrangement as described above referring to FIGS. 1, 3a and 5. The elevator comprises an elevator car C and a counterweight CW that are both vertically movable in a hoistway H, and said rope 1 is connected with the elevator car C and the counterweight CW. In this elevator there are ribs 2 present on only one side of the rope 1, because only one side of the rope 1 comes in contact with the rope wheels 4,40 of the elevator when running along its route. The elevator comprises an elevator arrangement comprising a belt-shaped rope 1 as illustrated in FIG. 1, and one or more rope wheels 4,40 (in this case two) provided with counterpart shape for the rope 1, in particular for a lateral side S1 thereof that is shaped to have elongated wedge-shaped ribs 2. The belt-shaped rope 1 is arranged to pass around rope wheels 4,40 such that a lateral side S1 of the rope 1 shaped to have elongated wedge-shaped ribs 2 engages the counterpart shape of each rope wheel 4,40. In the presented case, the elevator comprises a motor M and said rope wheels 4,40 comprise a drive wheel 4 rotatable with the motor M. The advantages related to the friction and groove factor are particularly important when the rope 1 is to be moved by rotation of the drive wheel 4, because the traction of the driven wheel is dependent on the friction and groove factor, and in general on all interaction between the drive rope wheel 4 and the rope 1. The rope wheels 4,40 are in the presented case mounted in proximity of the upper end of the hoistway H. The drive wheel 4 and the motor M can be mounted inside the upper end of the hoistway H whereby the elevator is machine-roomless, but alternatively they can be mounted inside a space beside or above the upper end of the hoistway H, for example, wherein said space can form a machine room of the elevator, for instance.

(42) FIG. 11 illustrates an elevator comprising an elevator arrangement as described above referring to FIGS. 2, 3b and 6. The elevator comprises an elevator car C and a counterweight CW that are both vertically movable in a hoistway H, and said at least one rope 1′ is connected with the elevator car C and the counterweight CW.

(43) The elevator comprises rope wheels 4,40,41 provided with a counterpart shape for a lateral side S1,S2 of the rope 1′ that is shaped to have elongated wedge-shaped ribs 2. The belt-shaped rope 1′ is arranged to pass around rope wheels 4,40,41 such that a lateral side S1, S2 of the rope 1′ shaped to have elongated wedge-shaped ribs 2 engages a counterpart shape of the rope wheel 4,40,41.

(44) The elevator presented in FIG. 11 is particularly of the type where the rope wheel 4,40,41 comprises two rope wheels 4,41, which have mutually nonparallel rotational axes, whereby the rope 1,1′ passing between these two rope wheels 4,41 has twist around its longitudinal axis. As visible in FIG. 11, one of these rope wheels is the drive wheel 4 mounted on a stationary structure (such as on the building or a structure mounted thereon e.g. a guide rail), and the other is a rope wheel mounted on the car C. Said two rope wheels 4,41 are each provided with a counterpart shape for the rope 1,1′, and the belt-shaped rope 1,1′ is arranged to pass around each of said two rope wheels 4,41 such that a lateral side S1, S2 thereof that is shaped to have elongated wedge-shaped ribs 2, engages a counterpart shape of the rope wheel 4,41 in question. The mutually nonparallel rotational axes are at a considerably large angle, the angle being in particular in the range 30-90 degrees, whereby the elevator is designed to have intentionally considerable twist in the belt-shaped rope. Ability to guide the ropes without problems with a large angle between the rotational axes, gives freedom to layout design. In the presented case, said range provides that the rope can turn around a rope wheel 4 along a plane extending beside the car C, and still pass to car C and be diverted to pass via the central area of the vertical projection of the car C. This provides that the suspension is made more central. The combination of hard surface material and sharp flank angle facilitate stability of rope system having rope twist as above described referring to FIG. 9.

(45) The belt-shaped rope 1′ of the elevator is as illustrated in FIG. 2. Accordingly, the opposite lateral sides S1, S2 of the belt-shaped rope 1′ are both shaped to have elongated wedge-shaped ribs 2 that are disposed adjacent each other in width direction w of the rope 1′ and extend parallel with the longitudinal direction 1 of the rope 1′, each said wedge-shaped rib 2 having a first flank face 2a and a second flank face 2b that are at an acute angle alfa relative to each other, and the surface material of said flank faces 2a, 2b has shore A hardness more than 85 and less than 100. Accordingly, in this elevator there are ribs 2 on two opposite sides S1,S2 of the rope 1′. This is advantageous, because in this elevator two opposite sides of the rope 1′ come in contact with the rope wheels 4,40 of the elevator when running along its route. As visible in FIG. 11, the elevator comprises two rope wheels 4,40, which are provided with a counterpart shape for the rope 1,1′, and said the belt-shaped rope 1,1′ is arranged to pass around said two rope wheels 4,40 such that one its lateral sides S1, S2 shaped to have elongated wedge-shaped ribs 2 engages the counterpart shape of one of the rope wheels 4,40, and the other of its lateral sides S1, S2 shaped to have elongated wedge-shaped ribs 2 engages the counterpart shape of the other of the rope wheels 4,40.

(46) In the elevator of FIG. 11, the elevator comprises a motor M and said rope wheels 4,40,41 comprise a drive wheel 4 rotatable with the motor M. The rope wheel 4 is in the presented case mounted inside the upper end of the hoistway H, which is advantageous as hereby the elevator is machine-roomless. As mentioned, the belt-shaped rope 1′ of the elevator is in this preferred embodiment as illustrated in FIG. 2, because this is advantageous for the reverse-bending configuration realized between rope wheels 4 and 40. However, alternatively also this elevator could be implemented using the rope 1 of FIG. 1. The advantages related to twist taking place between rope wheels 4 and 41 can be obtained irrespective of whether the rope is in accordance with FIG. 1 or 2. This is because the side of the rope 1′ to be placed against the rim of rope wheel 41 is preferably the same that is placed against the rim of the rope wheel 4.

(47) The elevators of FIGS. 10 and 11 preferably further comprises a control unit (not showed) for automatically controlling rotation of the motor M, whereby the movement of the car C is also made automatically controllable. In elevators of FIGS. 10 and 11, the rope 1,1′ is a suspension rope 1,1′ arranged to suspend the elevator car C, and belongs to a suspension roping comprising one or more suspending ropes for suspending the elevator car C.

(48) The rope wheel 4 comprises elongated wedge-shaped grooves 5 that are disposed adjacent each other in axial direction x of the rope wheel 4 and extend along the circumference of the rope wheel 4 parallel with each other, and the ribs 2 of the rope 1 extend into grooves 5 of the rope wheel 4. Each said groove 5 is delimited by flank faces 6a, 6b of neighboring ribs 6 that are at an acute angle (alfa) relative to each other.

(49) In the preferred embodiments, an advantageous structure for the load bearing member 10 and the rope 1 has been disclosed. However, the invention can be utilized with also other kind of the load bearing members and rope constructions such as with those of different materials and/or shapes. The load bearing member(s) 10 are most preferably made of composite material as described. However, they can in principle be made of alternative materials, such as in the form of twisted steel wire cords or twisted aramid fiber cords.

(50) The number of ribs 2 of the at least one of the lateral sides is preferably five or more. Hereby, firm engagement can be ensured and size of the grooves and ribs maintained small. However, the number can of course also be designed smaller, such as 2, 3, or 4.

(51) In the illustrated embodiments, the load bearing members 10 are substantially rectangular and larger in width direction than thickness direction. However, this is not necessary as alternative shapes could be used. Likewise, it is not necessary that the number of the load bearing members is four which is used for the purpose of the example. The rope 1 may of course be modified to have some other number of said load bearing members 1, such as 1, 2, 3, 5 or six or more.

(52) In FIGS. 10 and 11, the suspension ratios 1:1 and 2:1 have been illustrated. The rope 1,1′ could alternatively be implemented in any other kind of elevator, such as an elevator of 4:1 suspension ratio.

(53) As mentioned, the rope 1,1′ is preferably a suspension rope. However, each rope 1,1′ can alternatively be used as a compensation rope or an overspeed governor rope or an elevator. It is preferable, that the angles of grooves and ribs of the rope wheel are exactly the same as the angles of grooves and ribs of the rope. However, this is not absolutely necessary as it is possible to gain one or more of the advantages at least partially even though the shapes do not match completely. This is true for example when the mating faces only slightly differ in angle or shape.

(54) In the embodiment of FIG. 2, there are the same number of ribs on sides S1,S2. However, this is not necessary as alternatively there can be different number of ribs on said sides S1,S2.

(55) In the examples, each rope wheel 4,40,41 is suitable for engagement with at least one rope 1,1′. The vertical lines on left and right in FIG. 4-6 have been drawn dashed to indicate that the ribbed shape of the rope wheel 4,40,41 could continue left and/or right such that several ropes 1,1′ can be engaged with the one and same rope wheel 4,40,41.

(56) As mentioned earlier, the hardness properties of the surface material can be adjusted to the desired values with additives or particles added to the polymer serving as base material. Optionally, particles can also be provided in the surface material in order to roughen the surface of the rope 1,1′ which may be advantageous for adjusting the friction properties further.

(57) The aforementioned rope wheels 4,40,41 can be metallic or non-metallic. The flank faces 6a, 6b of the rope wheels 4,40,41 can be smooth or there can be transversal grooves (depth>0.2 mm) on the flank faces 6a, 6b to collect dirt that enables good friction if the rope wheel 4,40,41 collect dust, particles, etc. Due to the grooves to collect dirt the contact remains although the rope wheel gets dirty since the dirt accumulates on the bottom of the grooves.

(58) The hardness values defined in this application refer to values as measured in standard atmospheric conditions with temperature 20° C. and pressure 1 atm (101.325 kPa).

(59) It is to be understood that the above description and the accompanying Figures are only intended to teach the best way known to the inventors to make and use the invention. It will be apparent to a person skilled in the art that the inventive concept can be implemented in various ways. The above-described embodiments of the invention may thus be modified or varied, without departing from the invention, as appreciated by those skilled in the art in light of the above teachings. It is therefore to be understood that the invention and its embodiments are not limited to the examples described above but may vary within the scope of the claims.