Abstract
The invention relates to a drive machinery for an elevator, the drive machinery comprising a rotatable drive sheave for driving plurality of ropes of the elevator, and a motor for rotating the drive sheave; the drive sheave comprising a drive sheave body rotatable around a rotational axis; and plurality of rim arrangements mounted on the drive sheave body side by side in direction of said rotational axis, each said rim arrangement defining a circular outer rim for transmitting traction to a rope, said circular outer rims being coaxial with each other. The diameter of the circular outer rim of one or more of said rim arrangements is individually adjustable for enlarging or reducing the turning radius of a rope passing around the circular outer rim in question. The invention also relates to an elevator comprising said drive machinery.
Claims
1. A drive machinery for an elevator, the drive machinery comprising: a rotatable drive sheave configured to drive a plurality of ropes of the elevator, and a motor configured to rotate the rotatable drive sheave, wherein the rotatable drive sheave includes, a drive sheave body rotatable around a rotational axis, a plurality of rim arrangements mounted on the rotatable drive sheave body side-by-side in direction of said rotational axis, the plurality of rim arrangements defining circular outer rims for transmitting traction to a rope, the circular outer rims being coaxial with each other, the plurality of rim arrangements each including at least one rim member, and an adjusting device including a wedge and an actuator, the actuator configured to actuate the wedge radially against the at least one rim member to adjust diameters of each of the circular outer rims individually to enlarge or reduce a turning radius of a respective one of the plurality of ropes that pass therearound without changing the diameters of other ones of the circular outer rims.
2. The drive machinery according to claim 1, wherein the adjusting device is configured to individually adjust the diameter of a respective one of the circular outer rims relative to the diameters of the other ones of the circular outer rims.
3. The drive machinery according to claim 1, wherein the adjusting device is mounted on the rotatable drive sheave body such that the adjusting device is rotatable together with the rotatable drive sheave body around the rotational axis.
4. The drive machinery according to claim 1, wherein the adjusting device is electrically controllable.
5. The drive machinery according to claim 1, wherein the adjusting device is configured to change a position of the at least one rim member defining the respective one of the circular outer rims in a radial direction of said rotational axis.
6. The drive machinery according to claim 1, wherein the wedge is in a radial direction between the rotational axis and the at least one rim member of a respective one of the plurality of rim arrangements, the wedge is movable relative to the at least one rim member forward for wedging the at least one rim member radially outwards from said rotational axis, and backwards for releasing said wedging and for making way for the at least one rim member to move radially towards said rotational axis, and the actuator is configured to actuate movement of the wedge forward and backwards.
7. The drive machinery according to claim 1, wherein the actuator is an electric motor or a hydraulic cylinder.
8. The drive machinery according to claim 7, wherein said actuator is the electric motor, the electric motor configured to, rotate in one direction to move the wedge forward in first direction of said rotational axis, and rotate an opposite direction to move the wedge backwards in second direction of said rotational axis.
9. The drive machinery according to claim 1, wherein the wedge includes a pair of wedges, the actuator configured to move the pair of wedges in a direction of said rotational axis simultaneously towards each other to simultaneously wedge a rim member radially outwards from said rotational axis, and move the pair of wedges in the direction of said rotational axis simultaneously away from each other to simultaneously release said wedging and making way for a rim member to move radially towards said rotational axis.
10. The drive machinery according to claim 1, wherein each of the at least one rim member has a threaded radially inner side portion which is slanted and meshes with a threaded slanted radially outer side portion of the wedge, and the wedge is rotatable by the actuator relative to the at least one rim member.
11. An elevator comprising: the drive machinery as defined in claim 1, and the plurality of ropes arranged to pass around the rotatable drive sheave thereof while resting on a circular outer rim of one of the plurality of rim arrangements of the rotatable drive sheave.
12. The elevator according to claim 11, wherein the elevator further comprises: a tension sensor configured to sense individual tensions of one or more of the ropes, wherein the adjusting device is configured to adjust the diameter of the circular outer rim of at least one of the plurality of rim arrangements based on the individual tensions sensed by the tension sensor.
13. A rotatable drive sheave configured to drive a plurality of ropes of an elevator, the rotatable drive sheave comprising: a drive sheave body rotatable around a rotational axis; a plurality of rim arrangements mounted on the rotatable drive sheave body side-by-side in a direction of said rotational axis, the plurality of rim arrangements defining circular outer rims for transmitting traction to a rope, the circular outer rims being coaxial with each other, the plurality of rim arrangements each including at least one rim member; and an adjusting device including a wedge and an actuator, the actuator configured to actuate the wedge radially against the at least one rim member to adjust diameters of each of the circular outer rims individually to enlarge or reduce a turning radius of a respective one of the plurality of ropes that pass therearound without changing the diameters of other ones of the circular outer rims.
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 drive machinery for an elevator according to a preferred embodiment.
(3) FIG. 2 illustrates a schematically adjustability of an adjustable rim arrangement of FIG. 1 as seen in direction of the rotational axis of the drive sheave.
(4) FIG. 3 illustrates an embodiment of an elevator implementing the drive machinery of FIG. 1.
(5) FIG. 4 illustrates preferred details of the rope utilized in combination with the drive machinery of FIG. 1.
(6) FIGS. 5 and 6 illustrate different ways to form a circular outer rim of an adjustable rim arrangement of FIG. 1.
(7) FIG. 7 illustrates preferred details of a first kind for the drive machinery of FIG. 1.
(8) FIGS. 8a and 8b illustrates preferred details of a second kind for the drive machinery of FIG. 1.
(9) FIG. 9 illustrates preferred details of a third kind for the drive machinery of FIG. 1.
(10) FIG. 10 illustrates preferred details of a fourth kind for the drive machinery of FIG. 1.
(11) FIG. 11 illustrates preferred details of a fifth kind for the drive machinery of FIG. 1.
(12) FIG. 12 illustrates preferred details of a sixth kind for the drive machinery of FIG. 1.
(13) FIG. 13 illustrates preferred details connections between parts of an elevator.
(14) FIGS. 14a and 14b illustrate preferred details for facilitating deformation of a rim member of an adjustable rim arrangement particularly to be used in an embodiment in accordance with FIG. 5.
(15) The foregoing aspects, features and advantages of the invention will be apparent from the drawings and the detailed description related thereto.
DETAILED DESCRIPTION
(16) FIG. 1 illustrates a drive machinery M for an elevator according to a preferred embodiment. The drive machinery M comprises a rotatable drive sheave 1 for driving plurality of ropes 2 of the elevator, and a motor m for rotating the drive sheave 1. The motor m is preferably an electric motor. The drive sheave 1 comprises a drive sheave body 3 rotatable around a rotational axis X. The drive sheave 1 moreover comprises a plurality of rim arrangements 4A mounted on the drive sheave body 3 side by side in direction of said rotational axis X, each said rim arrangement 4A defining a circular outer rim 5 for transmitting traction to a rope 2, and on which circular outer rim 5 a rope can be placed to rest. The outer rims 5 of the rim arrangements 4A are coaxial with each other. Said rotational axis X is a rotational axis of the circular outer rims 5.
(17) The drive machinery M is suitable for exerting traction via the rim arrangements 4A on the ropes 2 passing around them. In FIG. 1, the drive sheave 1 is arranged to exert traction via the rim arrangements 4A on the ropes 2 passing around them.
(18) The drive sheave body 3 and the plurality of rim arrangements 4A are connected to each other such that they are all together rotatable by the motor m around said rotational axis X.
(19) As schematically illustrated in FIG. 2, the diameter of the rim 5 of one or more of said rim arrangements 4A is individually (i.e. without changing diameters of the rims 5 of the other rim arrangements 4A) adjustable for enlarging or reducing the turning radius of a rope 2 passing around the rim 5 in question. The rim arrangements 4A, the outer rim diameter of which are individually adjustable, are also referred to by using term individually adjustable rim arrangements and term adjustable rim arrangements.
(20) Preferably, said rim members 4 are completely or at least substantially unrotatable around the rotational axis X relative to the drive sheave body 3. When no considerable relative rotation can occur between the rim members 4 and the drive sheave body 3, these can all be effectively rotated together. Here, by term substantially unrotatable it is meant that the rim arrangements 4A in question cannot rotate around the rotational axis X relative to the drive sheave body 3 more than 10 degrees.
(21) Preferably, the circular outer rims 5 of said rim arrangements 4A are completely or at least substantially unrotatable around the rotational axis X relative to each other. When no considerable relative rotation can occur between the circular outer rims 5, rope tensions cannot be equalized effectively by relative rotation between the circular outer rims 5. In this context, the diameter adjustment is particularly advantageous. Here, by term substantially unrotatable it is meant that the rim arrangements 4A in question cannot rotate around the rotational axis X relative each other more than 10 degrees.
(22) The individually adjustable diameter is particularly individually adjustable to become greater relative to the diameters of the circular outer rims 5 of the other rim arrangements 4A and/or to become smaller relative to the diameters of the circular outer rims 5 of the other rim arrangements 4A. It is moreover preferable that the individually adjustable diameter is individually adjustable to become greater than diameters of the circular outer rims 5 of all the other rim arrangements 4A of the drive sheave 1 and/or to become smaller than diameters of the circular outer rims 5 of all the other rim arrangements 4A of the drive sheave 1. Thus, the speed of a rope 2 passing around the circular outer rim 5 that is in this way individually adjustable, can be made to be the highest within the roping formed by the ropes 2 or the lowest within the roping formed by the ropes 2. Hereby, the tension of the rope 2 passing around the circular outer rim 5 in question can be affected quickly and individually. It is also preferable that the diameters of the circular outer rims 5 of the adjustable rim arrangements 4A are adjustable to become the same with each other, and preferably also the same as the diameters of the circular outer rims 5 of the rim arrangements 4A the diameters of which are not adjustable, if such exist. Hereby, all the circular outer rims 5 of the drive sheave 1 can be made to have the same diameter, which is a well working starting point for a new elevator being installed.
(23) FIG. 2 shows how the path of the rope 2 changes when the diameter of the outer rim 5 of a rim arrangement 4A is changed between d1 and d2. When with a given angular speed co, the diameter is increased from d1 to d2, the tangential speed is increased from V1 to V2. This means that the speed of the rope 2 passing around the outer rim 5 in question is increased from V1 to V2. When this kind of adjustment is made for an individual outer rim 5, the speed of the individual rope 2 passing around it is increased relative to other ropes of the system, when diameters of the rims 5 around which they travel are not also increased. Correspondingly, by reduction of the diameter of the outer rim 5, the speed of the rope 2 passing around it can be reduced. An advantage is that the tension values of the rope 2 in question existing on opposite sides of the drive sheave 1 can be brought towards the tension values of the other ropes existing on opposite sides of the drive sheave 1. Thus, by individual rim diameter adjustment rope tension variations generated during car movement (e.g. due to non-idealities existing in the elevator structures) can be reduced. This alleviates tension problems in the elevator system.
(24) In the preferred embodiment, each said rim arrangement 4A is suitable for transmitting traction to only one rope 2. This facilitates that the tension adjustment can be focused on only one rope.
(25) FIG. 3 illustrates a preferred embodiment of an elevator according to the invention. The elevator comprises a drive machinery M as described above and plurality of ropes 2 arranged to pass around the drive sheave 1 thereof.
(26) The elevator comprises a hoistway H, and an elevator car C vertically moveable in the hoistway H, and an elevator control 100, which is configured to automatically control the motor m of the machinery M. The elevator comprises plurality of ropes 2 passing around the drive sheave 1, each resting on an outer rim 5 of one or the rim arrangements 4A of the drive sheave 1.
(27) The elevator moreover comprises a counterweight CW and the ropes 2 interconnect the car C and counterweight CW. The drive sheave 1 engages the section of each rope 2 extending between the car C and counterweight CW.
(28) The maximal travel distance d of the elevator car C, that is the distance between the uppermost position and the lowermost position of the car C during elevator use to serve passengers, which are realized when the car C (in particular the sill thereof) is level with the uppermost landing (in particular the sill thereof) where the car C can be driven and when the car C (in particular the sill thereof) is level with the lowermost landing (in particular the sill thereof) where the car C can be driven, respectively, is preferably more than 100 meters, more preferably more than 200 meters, possibly more than 300 meters, because the longer the travel distance, the more advantageous the solution is.
(29) FIG. 4 illustrates preferred details of the rope 2. In this case, the rope 2 is such that it can rest on an outer rim 5 of one of the rim arrangements 4A of the drive sheave 1 such that little or virtually no slip can occur between the rope 2 and the outer rim 5 of the drive sheave 1. In the embodiment illustrated, this is due to the rope 2 comprising an outer surface material comprising polymer. More specifically, in the presented embodiment, the rope 2 comprises load bearing members 9 extending in longitudinal direction of the rope 2 throughout the length thereof and embedded in a coating 8 forming the outer surface of the rope 2. The coating 8 comprises polymer material such as polyurethane for example, or alternatively rubber or silicone. The coating 8 is in contact with the outer rim 5 of a rim member 4 of one of the rim arrangements 4A of the drive sheave 1. The rope 2 is moreover belt-shaped, i.e. substantially larger in width direction w than in thickness direction t, which increases firmness of engagement between it and the drive sheave 1. This rope-shape thereby in its part reduces likelihood of slip between the rope 2 and the outer rim 5 of the drive sheave 1, and thereby the presented solution is advantageous with this kind of rope 2. The belt can be a flat belt, for example. Likelihood of slip is even lower if the rope 2 has tooth pattern engaging counterpart tooth pattern of the outer rim 5 of a rim member 4 of the drive sheave 1, or if the rope 2 comprises a rib pattern of ribs parallel to longitudinal direction of the rope engaging counterpart rib pattern of the outer rim 5 of a rim member 4 of the drive sheave 1, said alternative and optional patterns being presented in FIG. 4 in broken lines 77 and 78. At least some of the advantages of the invention can be achieved also with other shapes and materials of the rope 2, such as with ropes having round cross-section and comprising an outer surface material comprising polymer. The invention may be advantageous also with an uncoated steel rope passing around an uncoated drive sheave. In this kind of context, the tension differences between ropes do not tend to rise very high due to slip. However, slip may cause wear on the ropes and the drive sheave. By reducing tension differences, the invention can also be used to reduce slip and thereby increase service life of an uncoated steel rope and an uncoated drive sheave.
(30) FIGS. 5 and 6 illustrates different ways to form the circular outer rim 5. These Figures each discloses schematically how said adjusting means 10,20,30,40,40,50,60 are suitable for changing position of the rim member(s) 4 or at least the position of the circular outer rim 5 defined by it/them in radial direction of said rotational axis X. These Figures each discloses a schematic cross sectional view of the parts of a rim arrangement 4A defining the circular outer rim 5. In the solution presented in FIG. 5, the rim arrangement 4A comprises a single rim member defining said circular outer rim 5. In this case, the one rim member 4 defining said circular outer rim 5 is deformable to have different diameters, which can be implemented by resilient material and/or structure. The change of diameter need not be necessarily large in the adjustment, so even slight deformability of the rim member 4 can be sufficient, depending on the case. The material can be some composite material or plastic material, for instance. Anyway, should the material of the rim member 4 be of a very rigid material such as metal, the structure is preferable to design to have thin material thickness such that the deformation is achievable without very high forces and without departing from elastic nature of the deformation. In the solution presented in FIG. 6, the rim arrangement 4A comprises more than one rim members 4 defining together said circular outer rim 5. In this case plurality of rim members 4 together form an array of rim members 4 each defining a segment of said circular outer rim 5 for transmitting traction to a rope 2. In the embodiment of FIG. 6, the rim members 4 do not need to be deformable.
(31) For the purpose of carrying out the adjusting of the diameters of the rims 5 of the adjustable rim arrangements 4A, said drive sheave 1 moreover comprises an adjusting means 10,20,30,40,50,60 for individually adjusting the diameter of the circular outer rim 5 of each of the adjustable rim arrangements 4A.
(32) Said adjusting means 10,20,30,40,50,60 are preferably electrically controllable. Said adjusting means are particularly preferably electrically controllable by an elevator control, which is configured to automatically control the motor for rotating the drive sheave of the machinery. For this purpose, said adjusting means 10,20,30,40,50,60 comprise one or more inputs i for an electrical control signal. An elevator control 100 is illustrated in FIGS. 3 and 10.
(33) FIGS. 7-9 illustrate preferred alternative embodiments for implementing the diameter adjustment by aid of wedging. In these embodiments, said adjusting means 10,20,30 comprises a wedging means 11,21,31 actuatable to wedge the rim members 4 (i.e. the aforementioned single rim member 4 or more than one rim members 4, which alone or together define said circular outer rim 5) of an adjustable rim arrangement 4A radially outwards from said rotational axis X, as well as to release said wedging, and an actuator 12,22,32 for actuating the wedging means 11,21,31. The drive machinery M preferably comprises this kind of parts per each adjustable rim arrangement 4A.
(34) In the embodiments of FIGS. 7-9, said wedging means 11,21,31 comprises a wedging member 11,21,31 positioned in radial direction between the rotational axis X and a rim member 4 of an adjustable rim arrangement 4A, which wedging member 11,21,31 is movable relative to the rim member 4 forward F for wedging the rim member 4 radially outwards from said rotational axis X, and backwards B for releasing said wedging and for making way for the rim member 4 to move radially towards said rotational axis X, and the actuator 12,22,32 is arranged to actuate movement of the wedging member 11,21,31 in forward and backwards direction F,B. These embodiments are different in that in the embodiments of FIGS. 7 and 8, said movement forward and backwards is oriented parallel with direction of said rotational axis X, and in the embodiment of FIG. 9 in tangential direction of said rotational axis X.
(35) In the embodiments of FIGS. 7-9 said wedging member 11,21,31 has a radially (i.e. in radial direction of the rotational axis X) outer side portion which is slanted, in particular to have a first end and a second end displaced in direction of the rotational axis X, which ends are at a different distances from the rotational axis X, said wedging member 11,21,31 being movable against a radially (i.e. in radial direction of the rotational axis X) inner side of the rim member 4 for wedging the rim member 4 radially outwards from said rotational axis X.
(36) In the embodiments of FIGS. 7 and 8a-8b, said rim member 4 has a radially inner side portion which faces the slanted radially outer side portion of the wedging member 11,21,31, and is also slanted, in particular to have a first end and a second end displaced in direction of the rotational axis X, which ends are at a different distances from the rotational axis X.
(37) Said wedging member 11,21,31 is preferably ring-shaped and surrounds the rotational axis X. Thus, it can be used to wedge the rim members 4, were there a single or an array of them (cf. FIGS. 5 and 6), evenly and with simple structure.
(38) In the embodiment of FIGS. 7 and 8a-8b, said wedging member 11,21 has a conical radially outer side. Likewise, said rim member 4 has a conical radially inner side, or the radially inner sides of the rim members 4 of the array, as described referring to FIG. 6, together define a conical shape.
(39) In the embodiment of FIGS. 7 and 8a-8b, the above described wedging can be caused by at least one wedging member 11,21. However, it is preferable that there are two wedging members 11,21 for acting on the same the rim member 4. This is preferably implemented moreover such that the two wedging members 11,21 have mutually opposite forward F direction and backwards B direction. This facilitates compactness of the overall structure. Moreover, this provides that at least part of the forces counteract each other, which makes it more simple to provide reaction forces for the wedging. In the embodiments of FIGS. 7 and 8a-8b, the wedging is arranged to be caused by moving the two wedging members 11,21 closer to each other and released by moving the two wedging members 11,21 further apart.
(40) In the embodiment of FIG. 7, said actuator 12 is a motor. Most preferably the motor is an electric motor, and rotation, preferably rotation speed and/or rotation direction, of the motor 12 is electrically controllable.
(41) The actuator 12, which is here a motor, is connected via at least one drive member 13 with the wedging means 11, in particular with a wedging member 11 thereof. Rotation of the motor 12 in one direction is arranged to move the wedging member 12 forward F in direction of said rotation axis X, and rotation of the motor in another direction (i,e. the direction opposite to said one direction) is arranged to move the wedging member 11 backwards B in direction of said rotational axis X.
(42) In the embodiment of FIG. 7, the actuator 12, i.e. the motor 12 can move the wedging member 11 by screwing. For this purpose, the aforementioned at least one drive member comprises a screw member 13 oriented in direction parallel with the rotation axis X, and the wedging member 11 comprises an internal thread engaging with an external thread of the screw member 13.
(43) In the embodiment of FIG. 7, the adjustment is implemented using two wedging members 11. Particularly, said adjusting means 10 comprises two of said wedging members 11 movable by the actuator 12 in direction of said rotational axis X simultaneously towards each other both simultaneously wedging the rim member 4 radially outwards from said rotational axis X and/or in direction of said rotational axis X simultaneously away from each other both simultaneously releasing said wedging and making way for the rim member 4 to move radially towards said rotational axis X.
(44) The slanted outer side portion of each of the wedging members 11 faces a slanted radially inner side of a rim member 4 of the adjustable rim arrangement 4A, and slanted portions of the rim members 4 acted on by the two wedging members 11 are mirror shaped with respect to the plane of rotation p of the drive sheave body 3 (the plane p in Figures to which the axis X is normal).
(45) In the embodiment illustrated, the two wedging members 11 share a drive member, which is in the presented case a screw member 13 extending through them, and each of said two wedging members 11 comprises an internal thread engaging with an external thread of the screw member 13. The internal threads of the two wedging members 11 and the external threads of the screw member 13 are mirror shaped with respect to the plane of rotation p of the drive sheave body 3. Thus, by rotation of the screw member 13 in one rotation direction, the two wedging members 11 move towards each other (each moving in direction F), and by rotation of the screw member 13 in the other rotation direction, the two wedging members 11 move away from each other (each moving in direction B). Actuator 12 can be immovably mounted on the drive sheave body 3, for instance. It is however possible to mount it alternatively immovably on the wedging member 11 (either one in Figures), in which case the screw member 13 need not be in threaded engagement with both of the two wedging members 11.
(46) In the embodiment of FIG. 7, the drive sheave 1 moreover comprises a blocking means 14a,14b for blocking relative rotation between the wedging member 11 and the circular rim member 4. In the illustrated embodiment, these blocking means 14a,14b comprise a blocking member 14a placed in a nest formed between the wedging member 11 and the rim member 4. The nest 14b is larger than the blocking member 14a for allowing relative movement between the wedging member 11 and the rim member 4 in direction of said rotational axis x in said wedging. Thus the blocking member 14a does not block the relative movement between the wedging member 11 and the rim member 4 in direction of said rotational axis x in said wedging.
(47) In the embodiment illustrated in FIGS. 8a and 8b, the rim member 4 of the adjustable rim arrangement 4A has a threaded radially inner side portion which is slanted and meshes with a threaded slanted radially outer side portion of the wedging member 21, and the wedging member 21 is rotatable by the actuator 22 relative to the rim member 4.
(48) In the embodiment illustrated in FIGS. 8a and 8b, the actuator 22 is a hydraulic cylinder connected with the wedging means 21, in particular with the wedging member 21 thereof. One of the extension and retraction of the hydraulic cylinder 22 is arranged to rotate the wedging member 21 relative to the rim member 4 in one rotation direction and move it forward F in direction of said rotational axis X guided by the threaded engagement between the rim member 4 and the wedging member 21 thereby wedging the rim member 4 radially outwards from said rotational axis X. The other of the extension and retraction of the hydraulic cylinder 22 is arranged to rotate the wedging member 21 relative to the rim member 4 in the other rotation direction and move the wedging member 21 backwards B in direction of said rotational axis X guided by the threaded engagement between the rim member 4 and the wedging member 21, thereby releasing said wedging and making way for the rim member 4 to move radially towards said rotational axis X. Relative rotation between the wedging member 21 and the rim member 4 could alternatively be implemented using a motor, such as an electric motor as described referring to FIG. 7.
(49) In the embodiment of FIGS. 8a-8b, the actuator 22, i.e. the hydraulic cylinder 22 can move the wedging member 23 by screwing. In the embodiment illustrated in FIGS. 8a and 8b, the adjustment is implemented using two wedging members 21. Particularly, said adjusting means 20 comprises two of said wedging members 21 rotatable by the actuator 22 relative to the rim member 4, and movable in direction of said rotational axis X simultaneously towards each other both simultaneously wedging the rim member 4 radially outwards from said rotational axis X and/or simultaneously away from each other both simultaneously releasing said wedging and making way for the rim member 4 to move radially towards said rotational axis X. The slanted and threaded radially outer side portion of each of the wedging members 21 then meshes with a slanted and threaded radially inner side portion of a rim member 4 of the adjustable rim arrangement 4a. These two wedging members 21 (including the threads and slanting shape) and parts of the rim member 4 that they contact (including the threads and slanting shape of the rim member), are then mirror shaped with respect to the rotation plane of the drive sheave body 3 (the plane p in FIG. 8a to which the axis X is normal), which also parallel to the rotation planes of the wedging members 21. Thereby, when the two wedging members 21 are rotated together in one direction relative to the rim member 4, they are at the same time screwed along the threads of the rim member 4 such that they move towards each other (each moving in direction F), and when they are rotated relative to the rim member 4 together in the other direction they are screwed along the threads of the rim member 4 such that they move away each other (each moving in direction B). The actuator 22 is preferably immovably or at least substantially immovably mounted on the drive sheave body 3.
(50) In the embodiment illustrated in FIGS. 8a and 8b, the drive sheave 1 moreover comprises a synchronizing means 24a, preferably at least one synchronizing member 24a, for synchronizing rotation of the aforementioned two wedging members 21. It is arranged to allow relative movement between the two wedging members 21 in direction of said rotational axis X and block relative rotation between the wedging members 21. The synchronizing member 24a can be for instance a bar oriented parallel with rotational axis X its one end extending in a hole formed in one of the two wedging members 21 and its other end extending in a hole formed in the other one of the two wedging members 21, wherein said hole is also oriented parallel with the rotational axis X.
(51) In the embodiment FIG. 9, the wedging member 31 has plurality of radially (i.e. in radial direction of the rotational axis X) outer side portions which are slanted, in particular to have a first end and a second end displaced in tangential direction of the rotational axis X, which ends are at different distances from the rotational axis X, said wedging member 31 being movable against a radially (i.e. in radial direction of the rotational axis X) inner side of the rim member 4 for wedging the rim member 4 radially outwards from said rotational axis X.
(52) In FIG. 9, the structure when in line with FIG. 5 has been shown. By broken lines the seams between consecutive rim members 4 have been drawn to illustrate the structure when in line with FIG. 6.
(53) The aforementioned single rim member 4 or the rim members 4 of the array together (as described referring to FIG. 6) of the adjustable rim arrangement 4a comprise(s) plurality of radially inner side portions which face the slanted radially outer side portion of the wedging member 31 and are also slanted, in particular to have a first end and a second end displaced in tangential direction of the rotational axis X, which ends are at a different distances from the rotational axis X.
(54) The wedging member 31 is movable relative to the rim member 4 or the rim members 4 of the array in tangential direction of said rotational axis X forward F for wedging the rim member(s) 4 radially outwards from said rotational axis X, and backwards B for releasing said wedging and for making way for the rim member 4 to move radially towards said rotational axis X, and the actuator 32 is arranged to actuate movement of the wedging member 31 in forward and backwards direction F,B. In the preferred embodiment, said actuator 32 is a hydraulic cylinder connected with the wedging member 31 and the drive sheave body. The aforementioned rim member 4 or the rim members 4 of the array are completely or at least substantially unrotatable around the rotational axis X relative to the drive sheave body 3, whereby relative movement can be ensured.
(55) One of the extension and retraction of the hydraulic cylinder 32 is arranged to rotate the wedging member 31 relative to each said rim member 4 in one rotation direction and move it forward F in tangential direction of said rotational axis X thereby wedging each said rim member 4 radially outwards from said rotational axis X. The other of the extension and retraction of the hydraulic cylinder 32 is arranged to rotate the wedging member 31 relative to each said rim member 4 in the other rotation direction and move the wedging member 31 backwards B in direction of said rotational axis X thereby releasing said wedging and making way for each said rim member 4 to move radially towards said rotational axis X. Relative rotation between the wedging member 31 and the rim member 4 or the array of them around the rotational axis could alternatively be implemented using a motor, such as an electric motor as described referring to FIG. 7.
(56) FIG. 10 illustrates a preferred alternative embodiment wherein the diameter adjustment is implemented by screwing. In this embodiment, the adjusting means 40 comprises, preferably per each said adjustable rim arrangement 4A, a screwing means 41a-41d actuatable to push the rim members 4 of the adjustable rim arrangement 4A (i.e. the aforementioned single rim member 4 or more than one rim members 4 together defining said circular outer rim 5 of the adjustable rim arrangement 4A) radially outwards from said rotational axis X. The screwing means 41a-41d actuatable are moreover actuatable to release said push. The adjusting means 40 moreover comprises an actuator 42 for actuating the screwing means 41a-41d.
(57) In the drive machinery M of FIG. 10, the actuator 42 is preferably an electric motor, and rotation, preferably rotation speed and/or rotation direction, of the motor 42 is electrically controllable. The actuator 42 is illustrated in FIG. 10 with broken line. The actuator 42 is preferably fixedly mounted on the drive sheave body 3.
(58) In the drive machinery M of FIG. 10, the screwing means 41a-41d comprises screws 41c rotatable by said actuator 42. Each said screw 41c is rotatable in two rotation directions by said actuator 42 around an axis a extending in radial direction of the rotational axis X. The axis a has been illustrated only for one of the screws 41c. The rotational axis of the motor 42 is parallel with said rotational axis X. The actuator 42 is arranged to rotate each of said screws 41c via a bevel gear mechanism 41a,41b.
(59) Each said screw 41c is arranged to push a rim member 4 radially outwards from said rotational axis X when rotated by the actuator in one rotation direction, and to release said push and make way for the rim member 4 to move radially back towards said rotational axis X when rotated by the actuator in the other rotation direction.
(60) Said actuator 42 is arranged to rotate each said screw 41c inside a threaded opening 41d provided on the drive sheave body 3, or alternatively an element mounted fixedly thereon, in one rotation direction for pushing a rim member 4 radially outwards from said rotational axis X, and in the other rotation direction for releasing said push and for making way for the rim member 4 to move radially back towards said rotational axis X. Said releasing and making way may include also pulling the rim member 4 to move radially back towards said rotational axis X.
(61) FIG. 11 illustrates a preferred alternative embodiment wherein the diameter adjustment is implemented by hydraulically deforming the rim member(s) of each adjustable rim arrangement 4A. In this embodiment, each of the rim members 4 (i.e. the aforementioned single rim member 4 or the aforementioned more than one rim members 4 together defining said circular outer rim 5 of an adjustable rim arrangement 4A) comprises a hydraulic chamber 51 containing hydraulic fluid 54, and a radially outer wall 4′ of the hydraulic chamber, the radially outer wall 4′ in particular bordering the hydraulic chamber 51 on the radially outer side thereof, the shape of which radially outer wall 4′ is elastically deformable. The adjusting means 50 comprises a pressure adjusting system 52,53 for adjusting the fluid pressure, in particular increase or relieve the fluid pressure, in the hydraulic chamber 51 of the rim member 4. The pressure adjusting system 52,53 can for instance comprise a pressurizing device 52 (schematically shown), such as a hydraulic pump or a hydraulic cylinder connected by at least one fluid channel 53 with each hydraulic chamber 51 of the adjustable rim arrangement 4A. The pressure adjusting system 52,53 can possibly also comprise valves for controlling fluid flow and/or fluid pressure.
(62) The pressure adjusting system 52,53 is operable to increase the fluid pressure in said hydraulic chamber 51 such that the radially outer wall 4′ bulges radially outwards from said rotational axis X, as well as to relieve said pressure, in particular such that the radially outer wall 4′ retracts from a bulging state radially back towards said rotational axis X.
(63) FIG. 12 illustrates another preferred alternative embodiment wherein the diameter adjustment is implemented by hydraulically deforming the rim member(s) 4 of each adjustable rim arrangement 4A. In this embodiment, each of the rim members 4 (i.e. the aforementioned single rim member 4 or the more than one rim members 4 together defining said circular outer rim 5) of an adjustable rim arrangement 4A comprises plurality of hydraulic chambers 61 containing hydraulic fluid 64, and a radially outer wall 4′ of the hydraulic chamber, the radially outer wall 4′ in particular bordering the hydraulic chambers 61 on the radially outer side thereof, the shape of which radially outer wall 4′ is elastically deformable, and a pressure adjusting system 62,63 for adjusting fluid pressures in the hydraulic chambers 61 of the rim member 4 of the adjustable rim arrangement 4A. The pressure adjusting system 62,63 can for instance comprise a pressurizing device 62 (schematically shown), such as a hydraulic pump or a hydraulic cylinder connected by at least one fluid channel 63 with each hydraulic chamber 61 of the adjustable rim arrangement 4A. The pressure adjusting system 62,63 can possibly also comprise valves for controlling fluid flow and/or fluid pressure.
(64) The pressure adjusting system 62,63 is operable to increase the fluid pressure in each of the hydraulic chambers 61 of a rim member 4 such that the radially outer wall 4′ bulges radially outwards from said rotational axis X, as well as to relieve said pressure, in particular such that the radially outer wall 4′ retracts from a bulging state radially back towards said rotational axis X.
(65) The aforementioned plurality of hydraulic chambers 61 of a rim member 4 are preferably beside each other in direction of said rotational axis X, as illustrated in FIG. 12.
(66) The fluid pressures in the hydraulic chambers 61 of the rim member 4 are preferably adjustable to differ from each other.
(67) For facilitating adjustability of the fluid pressures in the hydraulic chambers 61 of the rim member 4 to differ from each other, in the preferred embodiment, fluid pressures in the plurality of hydraulic chambers 61 are individually adjustable by the pressure adjusting system 62,63, i.e. the pressure adjusting system 62,63 can adjust the fluid pressure, in particular increase or relieve the fluid pressure, in each of the hydraulic chambers 61 of the rim member 4 without changing fluid pressures in the other hydraulic chambers (61) of the rim member 4.
(68) For facilitating adjustability of the fluid pressures in the hydraulic chambers 61 of the rim member 4 to differ from each other, in the preferred the pressure adjusting system 62,63 preferably comprises fluid channels 63 separately connected with the hydraulic chambers 61 of the rim member 4 for enabling adjusting the fluid pressures in the hydraulic chambers 61 of the rim member 4 to differ from each other.
(69) The above mentioned adjustability of the fluid pressures in the hydraulic chambers 61 of the rim member 4 to differ from each other provides an additional advantage that the profile of the rim member 4 can be adjusted to control the position of the rope 2 in direction of the rotational axis X. The amount of camber of the profile of the rim member 4 can be increased or decreased by which camber the rope can be guided in direction of said rotational axis X towards the peak of the convex shaped profile. Asymmetry of the profile of the rim member 4 relative to plane of rotation p of the drive sheave body 3 can also be increased or decreased, by which asymmetry the rope can be guided towards a desired location in direction of said rotational axis X.
(70) In the embodiments of FIGS. 11 and 12, the drive sheave 1 can have a hydraulic pressurizing device 52,62 per each said adjustable rim arrangement 4A, but this is not necessary since hydraulic pressure can be shared for implementing adjustment of more than one adjustable rim arrangements 4A, particularly since it is possible to pressurize a fluid by a single pressurizing device, such as a pump or a hydraulic cylinder, and to connect the fluid with plurality of hydraulic chambers, and to use control valves between the pressurizing device and each hydraulic chamber which control valves are adjustable to reduce the fluid pressure individually.
(71) As mentioned above, the diameter of the rim 5 of one or more of said rim arrangements 4A is individually adjustable for enlarging or reducing the turning radius of a rope 2 passing around the rim 5 in question. Most preferably, the diameter of the rim 5 of more than one, possibly all or all but one, of said plurality of rim arrangements 4A is individually adjustable for enlarging or reducing the turning radius of a rope 2 passing around the rim 5 in question. The drive machinery M can for instance comprise 2, 3, 4, 5, 6, 7, 8, 9 or 10 rim arrangements 4A, and the diameter of the circular outer rim 5 of all or all but one of these rim arrangements 4A is individually adjustable for enlarging or reducing the turning radius of a rope 2 passing around the circular outer rim 5 in question.
(72) In the preferred embodiments, the motor m is connected with the drive sheave body 3, preferably directly or via transmission, such that the motor m can rotate the drive sheave body 3. The drive sheave body 3 is preferably either directly fixed to or integral with the rotor r of the motor m. Alternatively, there could be a force transmission, such as gears, between the motor m and the drive sheave body 3. Said adjusting means 10,20,30,40,50,60 are preferably mounted on the drive sheave body 3 such that they are rotatable together with the drive sheave body 3 around said rotational axis X.
(73) Generally, said releasing (i.e. releasing of the wedging and/or the push) and making way may for a rim member 4 to move radially towards said rotational axis X may include also pulling the rim member 4 to move radially back towards said rotational axis X. This can be simply implemented by mechanically connecting parts to each other radially immovably or at least substantially immovably. For example, this can be implemented by mechanically connecting the wedging means 11,21,31, such as the wedging member 11,21,31 thereof, radially immovably or at least substantially immovably to the rim member 4 or by mechanically connecting the screwing means, such as the screw 41c thereof, radially immovably or at least substantially immovably to the rim member 4.
(74) The elevator is preferably such that it comprises a tension sensing means s for sensing individual tensions of one or more of the ropes 2, and the elevator is arranged to adjust with said adjusting means 10,20,30,40,50,60 the diameter of the circular outer rim 5 of at least one adjustable rim arrangement 4A based on the sensed individual tensions 2. As illustrated in FIG. 3 said tension sensing means can comprise a force sensor s between the elevator car c and an end of a rope 2 fixed to the elevator car c for sensing individual tension of said rope 2 and/or a force sensor between the counterweight and an end of a rope fixed to counterweight for sensing individual tension of said rope 2. In a 2:1 solution, the force sensor(s) s would preferably be between an end of a rope fixed to a stationary fixing base (e.g. stationary structure of the building) on the elevator car c side for sensing individual tension of said rope 2 and/or between an end of a rope fixed to a stationary fixing base (e.g. stationary structure of the building) on the counterweight side for sensing individual tension of said rope 2. There are of course also alternative ways to measure tension of an individual rope.
(75) Preferably, the elevator is more particularly arranged to sense individual tensions of one or more of the ropes 2 and compare the sensed individual tensions with one or more reference tensions and to adjust by said adjusting means 10,20,30,40,50,60 the diameter of the circular outer rim 5 of at least one adjustable rim arrangement 4A based on the sensed individual tensions 2, in particular such that a difference between a measured tension and a reference tension is reduced.
(76) Said one or more reference tensions can comprises a preset tension or an average tension of measured individual tensions of plurality of ropes or a measured individual tension of one of the other ropes of the elevator, for example.
(77) As earlier above mentioned, in the solution presented in FIG. 5, the adjustable rim arrangement 4A comprises a single rim member 4 defining said circular outer rim 5. In this case, the one rim member 4 defining said circular outer rim 5 is deformable to have different diameters, which can be implemented by resilient material and/or structure. The deformability of the circular outer rim 5 to have different diameters can be facilitated structurally for instance by providing the rim member(s) of an adjustable rim arrangement 4A with plurality of cavities cv as illustrated in FIGS. 14a and 14b. In these Figures, preferred although not necessary further features are presented, namely that the rim member 4 comprises cavities cv. In the presented case, the rim member 4 comprises plurality of cavities cv side by side in the rotational direction X distributed along the rim 5 in tangential direction thereof. In the presented case, the cavities are elongated and oriented in tangential direction of the rim 5.
(78) 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.
