阅读说明：本技术 电梯驱动机构和电梯 (Elevator driving mechanism and elevator ) 是由 J·赫勒纽斯 R·佩尔托-休科 于 2019-08-08 设计创作，主要内容包括：本公开的实施例涉及电梯驱动机构和电梯。本发明涉及一种用于电梯的驱动机构(M),所述驱动机构包括用于驱动电梯的多个绳索(2)的可旋转驱动槽轮(1),以及用于旋转驱动槽轮(1)的马达；驱动槽轮(1)包括可围绕旋转轴线(X)旋转的驱动槽轮主体(3)以及多个轮辋装置(4A),多个轮辋装置(4A)沿旋转轴线(X)的方向并排安装在驱动槽轮主体(3)上,每个轮辋装置(4A)限定用于将牵引力传递至绳索(2)的圆形外轮辋(5),圆形外轮辋(5)彼此同轴。一个或多个轮辋装置(4A)的圆形外轮辋(5)的直径可单独调节,以增大或减小所讨论的绕过圆形外轮辋(5)的绳索(2)的转弯半径。本发明还涉及一种包括所述驱动机构的电梯。(Embodiments of the present disclosure relate to an elevator drive mechanism and an elevator. The invention relates to a drive mechanism (M) for an elevator, which drive mechanism comprises a rotatable drive sheave (1) for driving a plurality of ropes (2) of the elevator, and a motor for rotating the drive sheave (1); the drive sheave (1) comprises a drive sheave body (3) rotatable about a rotation axis (X) and a plurality of rim devices (4A), the plurality of rim devices (4A) being mounted side by side on the drive sheave body (3) in the direction of the rotation axis (X), each rim device (4A) defining a circular outer rim (5) for transferring traction to the rope (2), the circular outer rims (5) being coaxial with each other. The diameter of the circular outer rim (5) of one or more rim sets (4A) is individually adjustable to increase or decrease the turning radius of the rope (2) passing around the circular outer rim (5) in question. The invention also relates to an elevator comprising said drive mechanism.)

1. A drive mechanism (M) for an elevator, which drive mechanism (M) comprises a rotatable drive sheave (1) for driving a plurality of ropes (2) of the elevator, and a motor (M) for rotating the drive sheave (1); the drive sheave (1) comprises:

a drive sheave body (3) rotatable about a rotation axis (X);

a plurality of rim devices (4A) mounted side by side on the drive sheave body (3) in the direction of the rotation axis (X), each rim device (4A) defining a circular outer rim (5) for transmitting traction to the rope (2), the circular outer rims (5) being coaxial to each other,

characterized in that the diameter (d1, d2) of the circular outer rim (5) of one or more of the rim devices (4A) can be individually adjusted to increase or decrease the turning radius of the rope (2) passing around the circular outer rim (5).

2. The drive mechanism (M) according to claim 1, wherein the individually adjustable diameters (d1, d2) are individually adjustable to become larger relative to the diameter of the circular outer rim (5) of the other rim arrangement (4A) and/or to become smaller relative to the diameter of the rim (5) of the other rim arrangement (4A).

3. The drive mechanism (M) according to any one of the preceding claims, wherein each rim device (4A) comprises: a single rim member (4) defining the circular outer rim (5), or more than one rim member (4) collectively defining the circular outer rim (5).

4. The drive mechanism (M) according to any of the preceding claims, wherein the drive sheave (1) comprises adjustment means (10, 20, 30, 40, 50, 60) for individually adjusting the diameter of the circular outer rim (5) of each of the adjustable rim devices (4A).

5. The drive mechanism (M) according to claim 4, wherein the adjustment device (10, 20, 30, 40, 50, 60) is mounted on the drive sheave body (3) such that it is rotatable together with the drive sheave body (3) about the axis of rotation (X).

6. The drive mechanism (M) according to any one of the preceding claims 4-5, wherein the adjusting means (10, 20, 30, 40, 50, 60) are electrically controllable.

7. A drive mechanism (M) according to any of the preceding claims 4-6, wherein the adjustment means (10, 20, 30, 40, 50, 60) is adapted to change the position of the rim member (4) defining the circular outer rim (5) of the adjustable rim arrangement (4A) in a radial direction of the rotation axis (X), or at least the position of the circular outer rim (5) defined by the rim member (4) in a radial direction of the rotation axis (X).

8. The drive mechanism (M) according to any one of the preceding claims 4 to 7, wherein the adjustment means (10, 20, 30) comprise

-wedging means (11, 21, 31) actuatable to: wedging the rim member (4) defining the circular outer rim (5) of an adjustable rim set (4A) radially outwardly from the axis of rotation (X) and releasing the wedging; and

an actuator (12, 22, 32) for actuating the wedging device (11, 21, 31).

9. The drive mechanism (M) according to claim 8, wherein the wedging device (11, 21, 31) comprises at least one wedging member (11, 21, 31), the wedging member (11, 21, 31) being located in a radial direction between the rotation axis (X) and a rim member (4) of an adjustable rim device (4A), the wedging member (11, 21, 31) being movable forward (F) relative to the rim member (4) so as to wedge the rim member (4) radially outward from the rotation axis (X), and the wedging member (11, 21, 31) being movable backward (B) relative to the rim member (4) so as to release the wedging and to give way to the rim member (4) so as to move it radially toward the rotation axis (X), and the actuator (12, 31), 22. 32) is configured to actuate a forward (F) movement and a backward (B) movement of said wedging member (11, 21, 31).

10. The drive mechanism (M) according to any one of the preceding claims 8-9, wherein the actuator (12, 22, 32) is an electric motor (12) or a hydraulic cylinder (22, 32).

11. The drive mechanism (M) according to any one of the preceding claims 8-10, wherein the actuator (12, 22) is a motor and rotation of the motor in one direction is configured to move the wedging member (11, 21) forward (F) in a first direction of the rotation axis (X) and rotation of the motor in the other direction, i.e. the opposite direction, is configured to move the wedging member (11, 21) backward (B) in a second direction of the rotation axis (X).

12. The drive mechanism (M) according to any one of the preceding claims 8-11, wherein the adjustment means (10) comprise two of said wedging members (11), said two wedging members (11) being movable by said actuator (12): simultaneously move towards each other in the direction of the rotation axis (X) so that the two wedging members simultaneously wedge the rim member (4) radially outwards from the rotation axis (X); and/or simultaneously move away from each other in the direction of the rotation axis (X) so that the two wedging members simultaneously release the wedging and give way for a rim member (4) to move it radially towards the rotation axis (X).

13. The drive mechanism (M) according to any one of the preceding claims 8-12, wherein each rim member (4) has a threaded radially inner portion which is inclined and which engages with an inclined threaded radially outer portion of the wedging member (21), and the wedging member (21) is rotatable relative to the rim member (4) by the actuator (22).

14. The drive mechanism (M) according to any one of the preceding claims 4-7, wherein the adjustment device (40) comprises:

-screwing means (41a-41d), said screwing means (41a-41d) being actuatable to: pushing the rim member (4) defining the circular outer rim (5) of an adjustable rim set (4A) radially outwards from the axis of rotation (X) and releasing the pushing, and

an actuator (42) for actuating the screwing means (41a-41 d).

15. The drive mechanism (M) according to any one of the preceding claims 4-7, wherein each of the rim members (4) defining the circular outer rim (5) of the adjustable rim set (4A) comprises at least one hydraulic chamber (51, 61) containing a hydraulic fluid (54, 64), and a radially outer wall (4 '), the radially outer wall (4 ') bordering the hydraulic chamber (51), in particular on a radially outer side thereof, the radially outer wall (4 ') being elastically deformable in shape, and the adjustment device (50) comprising: a pressure regulating system (52, 53, 62, 63), such as a pressure regulating system comprising a pressurizing device (52, 62), for regulating a fluid pressure within the hydraulic chamber (51, 61), the pressure regulating system (52, 53, 62, 63) being operable to: increasing the fluid pressure within the at least one hydraulic chamber (51, 61) such that the radially outer wall (4') bulges radially outwards from the rotation axis (X); and releasing the pressure, in particular so that the radially outer wall (4') contracts radially back from the bulged state towards the axis of rotation (X).

16. Elevator comprising a drive mechanism (M) according to any of the preceding claims 1-15, and a plurality of ropes (2), which plurality of ropes (2) is configured to pass around its drive sheave (1), in particular each rope rests on a circular outer rim (5) of one of the rim devices (4A) of the drive sheave (1).

17. Elevator according to claim 16, wherein the elevator comprises a tension sensing device for sensing the individual tension of one or more of the ropes (2), the elevator being configured to adjust the diameter of the circular outer rim (5) of at least one adjustable rim device (4A) based on the sensed individual tension (2), in particular by means of an adjusting device (10, 20, 30, 40, 50, 60).

Technical Field

The present invention relates to an elevator drive mechanism and an elevator using the same. The elevator is preferably an elevator for transporting passengers and/or goods.

Background

Elevators typically include a drive sheave and a roping including ropes that are connected to the elevator car and pass around the drive sheave. Traction can be transferred from the drive sheave to the car via the ropes. Thus, car movement can be achieved and controlled by the drive sheave. For example, the drive sheave may be rotated by an electric motor.

The ropes driven by the drive sheave are usually connected to the elevator car on one side of the drive sheave and to the counterweight on the other side.

Traction sheave elevators tend to have more or less uneven rope forces. Ideally, the parallel ropes should have equal forces, but in practice there are rope force differences in the elevator due to non-ideal conditions, such as rope thickness variations, rope stiffness variations, rope coating thickness variations or rope groove diameter variations. If there is a difference in the turning diameter (e.g. pitch diameter) of the elevator ropes, the ropes will experience a difference in travel when the elevator is running. This will produce non-uniformity in the parallel rope force.

High friction ropes, such as ropes with a polymer coating, are particularly susceptible to large force variations due to small sliding on the drive sheave. The large rope force variations that occur on each traverse result in excessive fatigue loads on the load bearing components (e.g., the rope mount, the rope itself, and the guide shoe). Meanwhile, the problem of operation comfort is caused, the abrasion rate of the pulley is increased, and the service life of the rope is shortened. The ropes forcibly engaged with the driving sheave also face the problem of variations in rope force.

There are already known solutions for equalizing the rope tension on the individual ropes of a roping, wherein a rope tension equalizer is provided at the rope end. Such a solution has been proposed, for example, in document FI 84803B. Another known solution is to fix the rope end by means of a spring member, whereby the force is transferred from the rope to the fixed base by a spring moving the rope end relative to the fixed base. A disadvantage of these known solutions is that only a very limited range of movement of the rope end is allowed. When the end of the range is reached, the rope forces cannot be further equalized.

It has been noted that for high friction ropes, such as ropes with a polymer coating, there is little or no slip between the rope and the traction sheave, and therefore, unlike in the case of steel ropes, the stroke difference is difficult to compensate by slip. When the difference in travel is not compensated for, ropes with different free lengths have to be extended to the same length between the rope hitch plate and the traction sheave. The different elongations result in uneven rope forces, especially when the car or counterweight is near the top of the shaft, because in this case the suspension ropes are shorter and the stiffness is higher.

It is also noted that rope travel differences tend to accumulate with each rotation of the traction sheave. The long travel distance, small traction sheave and 2:1 suspension of the elevator increases the number of rotations of the sheave and worsens the problem. The smaller the overhead space, the shorter and stiffer the suspension ropes when the car or counterweight is at the top of the hoistway.

Thus, it has been noted that one drawback is that the ability of the existing solutions to equalize tension is the most problematic in elevators having one or more of the following situations: the travel distance is long, the sliding amount is small, the diameter of the traction sheave is small, the traction sheave is suspended in a ratio of 2:1, and the overhead space is small.

Disclosure of Invention

The object of the present invention is to provide an improved solution in respect of rope tension equalization of elevator ropes driven by a drive mechanism. It is an object, inter alia, to mitigate one or more of the above-mentioned disadvantages of the prior art, and/or problems discussed or suggested elsewhere in the specification. In particular a solution is presented by means of which an elevator with reduced variations in tension between the ropes can be implemented. In particular solutions are presented that can achieve this even if the elevator has one or more of the following situations (long travel distance, small amount of slip, small traction sheave diameter and 2:1 suspension, small overhead space).

The invention provides a novel driving mechanism for an elevator, which comprises a rotatable driving sheave, a plurality of ropes and a motor, wherein the ropes are used for driving the elevator; the drive sheave includes a drive sheave body rotatable about a rotational axis; and a plurality of rim devices mounted side by side on the drive sheave body in the direction of the rotation axis, each rim device defining a circular outer rim for transferring traction to a rope, in particular the rope can be placed on the circular outer rim to rest, the circular outer rims being coaxial with each other. The diameter of the circular outer rim of one or more rim sets can be adjusted individually (i.e. without changing the diameter of the rims of the other rim sets) to enlarge or reduce the turning radius of the rope passing through the circular outer rim in question.

With this solution it is possible to adjust the speed of a particular rope relative to the other ropes of the elevator, at which speed the ropes pass around the drive sheave from one side to the other. With the above-described solution, it is possible to eliminate tension differences between a specific rope and other ropes, for example, tension differences caused by changes in car position.

With this solution one or more of the above mentioned advantages and/or objects can be achieved. Preferred additional features are described below which may be combined with the drive mechanism, either individually or in any combination.

In a preferred embodiment, the rim member of the rim device is at least substantially non-rotatable relative to the drive sheave body about the axis of rotation.

In a preferred embodiment, the circular outer rims of the rim arrangement are at least substantially non-rotatable relative to each other about the axis of rotation.

In a preferred embodiment, the drive sheave body and the plurality of rim devices are connected to each other so as to be rotatable together about the axis of rotation by the electrodes.

In a preferred embodiment, the individually adjustable diameter is individually adjustable to be larger relative to the diameter of the circular outer rim of the other rim set and/or smaller relative to the diameter of the circular outer rim of the other rim set.

In a preferred embodiment, the individually adjustable diameter is individually adjustable to be larger relative to the diameter of the circular outer rim of all other rim sets and/or smaller relative to the diameter of the circular outer rim of all other rim sets.

In a preferred embodiment, each rim set is adapted to transmit traction to only one cable.

In a preferred embodiment, the above mentioned adjustability is possible during rotation of the drive sheave. That is, the diameter of the circular outer rim of one or more rim sets may be individually adjusted to increase or decrease the turning radius of the rope passing around the circular outer rim in question during rotation of the drive sheave.

In a preferred embodiment, each rim set comprises a single rim member defining a circular outer rim, or a plurality of rim members which together define a circular outer rim.

In a preferred embodiment the drive sheave further comprises adjustment means for individually adjusting (i.e. without changing the diameter of the rims of the other rim sets) the diameter of the circular outer rim of each of the one or more adjustable rim sets.

In a preferred embodiment, the motor for rotating the drive sheave is connected to the drive sheave body, preferably directly or via a transmission, so that the motor can rotate the drive sheave body. The drive sheave body is preferably directly fixed to or integrally formed with the rotor of the electric motor. Alternatively, a force transmission, such as a gear, may be provided between the motor and the drive sheave body.

In a preferred embodiment, the adjustment device is mounted on the drive sheave body so as to be rotatable together with the drive sheave body about the axis of rotation.

In a preferred embodiment, the adjustment means are controllable. The adjusting device is particularly preferably electrically controlled by an elevator controller, which is configured to automatically control the motor to rotate the drive sheave of the mechanism. Preferably, the adjustment means comprises an electrical control signal input means. The electrically controllable adjusting device allows a free choice of how and on which variables to adjust. This has the advantage that the control of the regulating device can be programmed to intelligently take into account any number of variables, analyze a number of variables and freely compare the variables. Preferably the control variable comprises the rope tension of the individual ropes of the elevator.

In a preferred embodiment, the adjustment device is adapted to change the position of a rim member (i.e. the above-mentioned rim member or members together) defining a circular outer rim of the adjustable rim device in a radial direction of the rotation axis, or at least the position of the circular outer rim defined by the rim members in a radial direction of the rotation axis.

In a preferred embodiment, the diameter adjustment is arranged to be effected by means of wedging. In a preferred embodiment using wedging, the adjustment means comprises (preferably for each adjustable rim set) wedging means actuable to wedge the rim members (i.e. the single rim member or a plurality of rim members described above) defining the circular outer rim of the adjustable rim set radially outwardly from the axis of rotation and release the wedging. Furthermore, the adjustment device comprises an actuator for actuating the wedging device. The adjustment means may comprise such an actuator for each adjustable rim set or, alternatively, a common actuator may be used to actuate wedging means for a plurality of adjustable rim sets.

In a preferred embodiment using wedging, the wedging device comprises at least one wedging member located in a radial direction between the rotational axis and a rim member of the adjustable rim set, the wedging member being movable forwardly relative to the rim member to wedge the rim member radially outwardly from the rotational axis and to move rearwardly to release the wedging and to clear the rim member for radial movement towards the rotational axis, and the actuator is arranged to actuate forward and backward movement of the wedging member.

In a preferred embodiment using wedging, the wedging device comprises at least one wedging member located in a radial direction between the rotation axis and a rim member of the adjustable rim device, the wedging member being movable forward in the direction of the rotation axis or a tangential direction to the rotation axis relative to the rim member to wedge the rim member radially outward from the rotation axis and rearward in the direction of the rotation axis or a tangential direction to the rotation axis to release the wedging and to give way to the rim member to move radially towards the rotation axis, and the actuator is arranged to actuate the forward and backward movement of the wedging member in the direction of the rotation axis or a tangential direction to the rotation axis.

In a preferred embodiment utilizing wedging, the wedging member has a radially outer portion (in the radial direction of the axis of rotation) that is inclined and movable against a radially inner portion of the rim member (in the radial direction of the axis of rotation) to wedge the rim member radially outward from the axis of rotation.

In a preferred embodiment utilizing wedging, the rim member has a radially inner portion that is inclined and faces the inclined radially outer portion of the wedging member.

In a preferred embodiment utilizing wedging, the wedging member is annular and surrounds the axis of rotation. Thus, it can be used to wedge into rim members, even and structurally simple, given that the rim members are single or an array of members.

In a preferred embodiment utilizing wedging, the wedging member has a tapered radially outer side.

In a preferred embodiment utilizing wedging, the individual rim members have a tapered radially inner side, or the radially inner sides of the array of rim members collectively define a tapered shape.

In a preferred embodiment utilizing wedging, the actuator is an electric motor or a hydraulic cylinder.

In a preferred embodiment utilizing wedging, the actuator is an electric motor and the rotation (e.g., speed and/or direction) of the motor is electrically controllable.

In a preferred embodiment using wedging, the actuator is connected to the wedging device, in particular to the wedging member of the wedging device, via at least one driving member.

In a preferred embodiment utilizing wedging, the actuator is an electric motor, such as an electric motor, and rotation of the motor in one direction is configured to move the wedging member forward in a first direction of the axis of rotation, and rotation of the electric motor in the other direction (i.e., the opposite direction) is configured to move the wedging member backward in a second direction of the axis of rotation.

In a preferred embodiment utilizing wedging, the wedging is caused by at least one wedging member. Preferably, however, the adjustment means comprises two wedging members for acting on the same rim member. Furthermore, it is preferably implemented such that the two wedging members have a forward direction and a backward direction opposite to each other.

In a preferred embodiment utilizing wedging, an actuator, such as a motor or hydraulic cylinder, can move the wedging member by screwing.

In a preferred embodiment utilizing wedging, the at least one drive member comprises a screw member oriented in a direction parallel to the axis of rotation and the wedging member comprises an internal thread that meshes with the external thread of the screw member.

In a preferred embodiment using wedging, the adjustment means comprise two wedging members which are simultaneously movable by the actuator towards each other in the direction of the rotation axis while wedging the rim member radially outwards from the rotation axis and/or away from each other in the direction of the rotation axis to release the wedging and to give way for the rim member to move radially towards the rotation axis.

In a preferred embodiment utilizing wedging, each rim member has a threaded radially inner portion that is inclined and engages a threaded inclined radially outer portion of the wedging member, and the wedging member is rotatable relative to the rim member by the actuator. For example, the actuator may be a motor, such as an electric motor or a hydraulic cylinder. Preferably, however, the actuator is a hydraulic cylinder connected to the wedging device, in particular to the wedging member of the wedging device. In this case, one of the expansion and contraction of the hydraulic cylinder is configured to rotate the wedging member in one rotational direction relative to the rim member and to move forward in the direction of the rotational axis guided by the threaded engagement between the rim member and the wedging member, thereby wedging the rim member radially outward from the rotational axis. The other of the extension and retraction of the hydraulic cylinder is configured to rotate the wedging member in the other rotational direction relative to the rim member and to move the wedging member rearwardly in the direction of the rotational axis guided by the threaded engagement between the rim member and the wedging member, thereby releasing the wedge and giving way to the rim member to move it radially toward the rotational axis.

In a preferred embodiment using wedging, the adjustment means comprises two wedging members which can be rotated relative to the rim member by an actuator, as previously described, the wedging members being movable in the direction of the axis of rotation simultaneously towards each other while wedging the rim member radially outwardly from the axis of rotation and/or simultaneously away from each other to release the wedging and to clear the rim member for radial movement towards the axis of rotation. In particular, the radially outer portion of the inclined threads of each wedge member then engages with the radially inner portion of the inclined threads of the rim member of the rim set.

In a preferred embodiment, the diameter adjustment is arranged to be effected by screwing. In a preferred embodiment using screwing, the adjustment means comprises (preferably for each adjustable rim device) a screwing device which can be actuated to urge the rim members defining the circular outer rim of the adjustable rim device (i.e. the above-mentioned rim member or members together) radially outwards from the axis of rotation and to release this urging. Furthermore, the device comprises an actuator for actuating the screwing device. The adjustment device may comprise such an actuator for each adjustable rim device or, alternatively, a common actuator may be used to actuate screwing devices of a plurality of adjustable rim devices. The actuator is preferably an electric motor. Then, preferably, the rotational speed and/or the rotational direction of the motor is electrically controllable.

In a preferred embodiment using screws, the screwing means comprise one or more screws that can be rotated by the actuator. Preferably, each screw is rotatable by the actuator in both rotational directions, most preferably about an axis extending in a radial direction of the rotational axis of the drive sheave body.

In a preferred embodiment using screws, the actuator is arranged to rotate each screw in one rotational direction, within a threaded opening provided on the drive sheave body, or an element mounted on the threaded opening, to urge the rim member radially outwardly from the axis of rotation, and in the other rotational direction to release the urging and to give way for the rim member to move radially rearwardly towards the axis of rotation of the drive sheave body.

In a preferred embodiment using screws, each screw is arranged to urge the rim member radially outwardly from the axis of rotation when rotated by the actuator in one rotational direction, and to release the urging and give way for the rim member to move radially rearwardly towards the axis of rotation X when rotated by the actuator in the other rotational direction.

In a preferred embodiment using screws, the actuator is arranged to rotate one or more screws via a bevel gear mechanism.

In a preferred embodiment using screws, the axis of rotation of the (actuator) motor is parallel to the axis of rotation of the drive sheave body.

In a preferred embodiment, the diameter adjustment is arranged to be effected by means of hydraulic technology. In a preferred embodiment using hydraulics, each rim member defining the circular outer rim of the adjustable rim set, i.e. the above-mentioned rim member or rim members together, comprises at least one hydraulic chamber containing hydraulic fluid, and a radially outer wall, which borders the hydraulic chamber, in particular on the radially outer side, the radially outer wall is elastically deformable in shape, and the device comprises a pressure regulating system, such as a pressure regulating system comprising hydraulic pressurizing means (e.g. a hydraulic pump or a hydraulic cylinder), for regulating the fluid pressure in the hydraulic chambers, in particular increasing or decreasing the fluid pressure, the pressure regulating system may be operable to increase the fluid pressure in one or more of the hydraulic chambers, such that the radially outer wall bulges radially outwards from the rotational axis, and releasing the pressure, in particular causing the radially outer wall to contract radially back from the bulged condition towards the axis of rotation.

In a preferred embodiment using hydraulics, each rim member (i.e. the single rim member or the plurality of rim members described above) defining the circular outer rim of the adjustable rim apparatus comprises a plurality of hydraulic chambers containing hydraulic fluid, and a radially outer wall interfacing with the hydraulic chambers, particularly on the radially outer side, the radially outer wall being resiliently deformable in shape, and the apparatus comprises a pressure regulating system, such as a pressure regulating system (e.g. a hydraulic pump or a hydraulic cylinder) comprising hydraulic pressurising means for regulating the fluid pressure within the hydraulic chambers, the pressure regulating system being operable to increase the fluid pressure within each hydraulic chamber, such that the radially outer wall bulges radially outwards from the axis of rotation, and to release the pressure, particularly such that the radially outer wall contracts radially backwards from the bulged state towards the axis of rotation. Preferably, the plurality of hydraulic chambers are adjacent to each other in the direction of the rotational axis of the drive sheave body.

In a preferred embodiment using hydraulics, the fluid pressures in the hydraulic chambers of the same rim member can be adjusted to be different from each other.

In a preferred embodiment using hydraulic technology, the pressure regulating system includes fluid passages respectively connected to the hydraulic chambers of the rim member for achieving regulation of the fluid pressures in the hydraulic chambers of the rim member to be different from each other.

In a preferred embodiment utilizing hydraulics, the fluid pressure in the plurality of hydraulic chambers can be individually regulated by a pressure regulation system, i.e., the pressure regulation system can regulate, in particular increase or decrease, the fluid pressure in each hydraulic chamber of the rim member without changing the fluid pressure in the other hydraulic chambers of the rim member.

A new elevator is also presented, comprising a drive mechanism as defined anywhere above, and a plurality of ropes arranged to pass over their respective drive sheaves, in particular to rest on the outer rim of one rim device of the drive sheaves, respectively. With this solution one or more of the above mentioned advantages and/or objects can be achieved. Preferred further features are presented below and in the context of the drive mechanism described above, these further features can be combined with the elevator either individually or in any combination.

In a preferred embodiment, the rope comprises a coating forming an outer surface of the rope, wherein the coating is in contact with an outer rim of one of the rim sets of the drive sheave, and the coating comprises a polymeric material.

In a preferred embodiment the elevator comprises a tension sensing means for sensing the individual tension of the one or more ropes, the elevator being arranged to adjust the diameter of the circular outer rim of the at least one adjustable rim means based on the sensed individual tension of the one or more ropes, preferably by means of the adjusting means described above.

In a preferred embodiment the elevator is arranged to sense individual tensions of one or more ropes and to compare the sensed individual tensions with one or more reference tensions and, based on the sensed individual tensions, to adjust the diameter of the circular outer rim of the at least one adjustable rim device by the adjusting device, in particular such that the difference between the measured tension and the reference tension is reduced.

In a preferred embodiment, the reference tension may comprise, for example, a preset tension or a measured individual tension average tension of a plurality of ropes, or a measured individual tension of one other rope of the elevator.

In a preferred embodiment, the elevator comprises a hoistway, an elevator car vertically movable in the hoistway, and an elevator controller configured to automatically control a motor of the machine.

In a preferred embodiment the maximum distance of travel of the elevator car is preferably more than 100 meters, more preferably more than 200 meters, most preferably more than 300 meters.

In a preferred embodiment, each cord is belt-shaped, i.e. much larger in the width direction than in the thickness direction. The width/thickness ratio of the rope is then preferably greater than 2.

In a preferred embodiment each rope is a flat belt or the rope has a tooth pattern which meshes with a corresponding tooth pattern of the outer rim of the circular rim member of the drive sheave, or the rope comprises a rib pattern of ribs parallel to the longitudinal direction of the rope which meshes with a corresponding rib pattern of the outer rim of the circular rim member of the drive sheave.

In a preferred embodiment, the adjusting means is an adjusting device.

The elevator generally preferably comprises an elevator car which is vertically movable to and from a plurality of landings, i.e. two and more vertically displaced landings. Preferably, the elevator car has an interior space adapted to accommodate one or more passengers, and the car may be provided with doors for forming an enclosed interior space.

Drawings

The invention will be described in more detail below, by way of example, with reference to the accompanying drawings, in which:

fig. 1 presents a drive mechanism of an elevator according to a preferred embodiment;

fig. 2 shows a schematic adjustability of the adjustable rim set of fig. 1 seen from the direction of the axis of rotation of the drive sheave;

fig. 3 presents an embodiment of an elevator implementing the drive mechanism of fig. 1;

FIG. 4 shows a preferred detail of a cord used in conjunction with the drive mechanism of FIG. 1;

FIGS. 5 and 6 illustrate different ways of forming the circular outer rim of the adjustable rim apparatus of FIG. 1;

FIG. 7 shows a first preferred detail of the drive mechanism of FIG. 1;

FIGS. 8a and 8b show a second preferred detail of the drive mechanism of FIG. 1;

FIG. 9 shows a third preferred detail of the drive mechanism of FIG. 1;

FIG. 10 shows a fourth preferred detail of the drive mechanism of FIG. 1;

FIG. 11 shows a fifth preferred detail of the drive mechanism of FIG. 1;

FIG. 12 shows a sixth preferred detail of the drive mechanism of FIG. 1;

fig. 13 shows a preferred connection detail between the parts of the elevator; and

fig. 14a and 14b show preferred details which facilitate the deformation of the rim member of the adjustable rim set, in particular for the embodiment according to fig. 5.

The foregoing aspects, features and advantages of the invention will be apparent from the accompanying drawings and from the detailed description thereof.

Detailed Description

Fig. 1 shows a drive machine M of an elevator according to a preferred embodiment. The drive mechanism M comprises a rotatable drive sheave 1 for driving a number 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, the drive sheave body 3 being rotatable about an axis of rotation X. The drive sheave 1 further comprises a plurality of rim devices 4A, the plurality of rim devices 4A being mounted side by side on the drive sheave body 3 in the direction of the rotation axis X, each rim device 4A defining a circular outer rim 5 for transferring traction to the rope 2, and the rope can be placed on the circular outer rim 5 to rest. The outer rims 5 of the rim set 4A are coaxial with each other. The axis of rotation X is the axis of rotation of the circular outer rim 5.

The drive mechanism M is adapted to apply traction to the rope 2 passing around the rim set 4A via the rim set 4A. In fig. 1, the drive sheave 1 is arranged to apply traction to the rope 2 passing around the rim arrangement 4A via the rim arrangement 4A.

The drive sheave body 3 and the plurality of rim devices 4 are connected to each other so that they can be rotated together about the rotation axis X by the motor m.

As schematically shown in fig. 2, the diameter of the rims 5 of one or more rim sets 4A can be individually adjusted (i.e. without changing the diameter of the rims 5 of the other rim sets 4A) to enlarge or reduce the turning radius of the rope 2 passing around the rim 5 in question. The rim set 4A in which the outer rim diameter can be adjusted individually may also be referred to as an individually adjustable rim set or an adjustable rim set.

Preferably, the rim member 4 is completely or at least substantially non-rotatable about the rotation axis X relative to the drive sheave body member 3. At this time, no significant relative rotation occurs between the rim member 4 and the drive sheave body 3, and these components can all effectively rotate together. Here, the term "substantially non-rotatable" means that the rim device 4A in question is not rotatable relative to the drive sheave body 3 about the axis of rotation X by more than 10 degrees.

Preferably, the circular outer rims 5 of the rim set 4A are completely or at least substantially non-rotatable with respect to each other around the rotation axis X. When no significant relative rotation between the circular outer rims 5 occurs, the rope tension cannot be effectively equalized by the relative rotation between the circular outer rims 5. In this case, diameter adjustment is particularly advantageous. Here, the term "substantially non-rotatable" means that the rim devices 4A in question are not rotatable relative to each other about the axis of rotation X through more than 10 degrees.

The individually adjustable diameter is particularly individually adjustable to be larger relative to the diameter of the circular outer rim 5 of the other rim set 4A and/or smaller relative to the diameter of the circular outer rim 5 of the other rim set 4A. More preferably, the individually adjustable diameter is individually adjustable to be larger relative to the diameter of the circular outer rim 5 of all other rim arrangements 4A of the drive sheave 1 and/or smaller relative to the diameter of the circular outer rim 5 of all other rim arrangements 4A of the drive sheave 1. Thus, the speed of the rope 2 passing around the circular outer rim 5, which is individually adjustable in this way, can be highest within the roping formed by the rope 2 or lowest within the roping formed by the rope 2. Thus, the tension of the rope 2 passing around the circular outer rim 5 in question can be influenced quickly and individually. It is also preferred that the diameters of the circular outer rims 5 of the adjustable rim set 4A can be adjusted to be the same as each other and preferably also the same as the diameter of the circular outer rim 5 of the non-adjustable rim set 4A (if present). Thus, all circular outer rims 5 of the drive sheave 1 can have the same diameter, which is a good starting point for installing a new elevator.

Figure 2 shows how the path of the cord 2 changes as the diameter of the outer rim 5 of the rim set 4A changes between d1 and d 2. At a given angular velocity ω, the diameter increases from d1 to d2 and the tangential velocity increases from V1 to V2. This means that the speed of the rope 2 passing around the outer rim 5 in question increases from V1 to V2. When this adjustment is made to a single outer rim 5 and the diameter of the rim 5 around which the rope travels does not increase, the speed of the single rope 2 passing around the rim increases relative to the other ropes of the system. Accordingly, by reducing the diameter of the outer rim 5, the speed of the rope 2 passing around the rim can be reduced. One advantage of this is that the tension value of the rope 2 present on the opposite side of the drive sheave 1 in question can be changed towards the tension values of the other ropes present on the opposite side of the drive sheave 1. Thus, by individual rim diameter adjustment, variations in tension generated during car movement (e.g., caused by non-idealities present in the elevator structure) may be reduced. This alleviates tension problems in the elevator system.

In a preferred embodiment, each rim set 4A is adapted to transmit traction to only one rope 2. This facilitates that the tension adjustment is concentrated on one rope only.

Fig. 3 presents a preferred embodiment of the elevator according to the invention. The elevator comprises a drive mechanism M as described above and a plurality of ropes 2, which ropes 2 are arranged to pass around its drive sheave 1.

The elevator comprises a hoistway H, and an elevator car C vertically movable in the hoistway H, and an elevator controller 100, the elevator controller 100 being configured as a motor M of an automatic control mechanism M. The elevator comprises a number of ropes 2 passing around the drive sheave 1, each rope resting on an outer rim 5 of one rim device 4A of the drive sheave 1.

The elevator also comprises a counterweight CW and ropes 2 interconnect the car C and the counterweight CW. The drive sheave 1 engages the portion of each rope 2 extending between the car C and the counterweight CW.

The maximum travel distance d of the elevator car C is the distance between the highest position and the lowest position of the car C when the elevator is used to serve passengers, which are achieved when the car C (in particular its sill) is level with the highest landing (in particular its sill) where the car can be driven and when the car C (in particular its sill) is level with the lowest landing (in particular its sill) where the car can be driven, respectively. The maximum travel distance d is preferably greater than 100 meters, more preferably greater than 200 meters, possibly greater than 300 meters, since the longer the travel distance, the more advantageous the solution.

Fig. 4 shows a preferred detail of the rope 2. In this case, the rope 2 may rest on the outer rim 5 of one rim device 4A of the drive sheave 1, so that there is little or no slip between the rope 2 and the outer rim 5 of the drive sheave 1. In the embodiment shown, this is because the rope 2 comprises an outer surface material comprising a polymer. More specifically, in the presented embodiment, the rope 2 comprises a load-bearing member 9, which load-bearing member 9 extends in the longitudinal direction of the rope 2 over its entire length and is embedded in a coating 8 forming the outer surface of the rope 2. The coating 8 comprises a polymeric material, such as polyurethane, or alternatively, rubber or silicone. The coating 8 is in contact with the outer rim 5 of the rim member 4 of one rim device 4A of the drive sheave 1. Furthermore, the ropes 2 are belt-shaped, i.e. much larger in the width direction w than in the thickness direction t, which increases the robustness of the engagement between the ropes 2 and the drive sheave 1. Thereby, such a rope shape reduces the possibility of slipping between the rope 2 and the outer rim 5 of the drive sheave 1, and therefore the proposed solution with such a rope 2 is advantageous. For example, the belt may be a flat belt. The possibility of slipping is even lower if the rope 2 has a toothing pattern which meshes with a corresponding toothing pattern of the outer rim 5 of the rim member 4 of the drive sheave 1, or if the rope 2 comprises a rib pattern of ribs which is parallel to the rope longitudinal direction and meshes with a corresponding rib pattern on the outer rim 5 of the rim member 4 of the drive sheave 1. The above described alternative and optional patterns are shown in fig. 4 by dashed lines 77 and 78. At least some of the advantages of the invention can also be achieved with ropes 2 of other shapes and materials, for example ropes having a circular cross-section and comprising an outer surface material comprising a polymer. The invention with uncoated steel cords passing around uncoated drive sheaves is also advantageous. In this case the tension difference between the ropes does not become very high due to slipping. However, slippage may cause wear on the ropes and drive sheaves. By reducing the tension differential, the present invention can also be used to reduce slippage, thereby extending the service life of uncoated wire ropes and uncoated drive sheaves.

Figures 5 and 6 show different ways of forming the circular outer rim 5. These figures disclose schematically how the adjustment devices 10, 20, 30, 40, 50, 60, respectively, are adapted to change the position of the rim member 4 or at least the position of the circular outer rim 5 defined by the rim member/members in radial direction of the rotation axis X. These figures each disclose a schematic cross-sectional view of a portion of a rim set 4A defining a circular outer rim 5. In the solution shown in figure 5, the rim set 4A comprises a single rim member defining a circular outer rim 5. In this case, one rim member 4 defining the circular outer rim 5 may be deformed to have different diameters, which may be achieved by an elastic material and/or structure. The change in diameter at the time of adjustment is not necessarily large, and therefore, depending on the case, even a slight deformation capability of the rim member 4 may be sufficient. For example, the material may be some composite material or a plastic material. In any event, if the material of the rim member 4 is a very rigid material, such as metal, the structure is preferably designed with a small material thickness so that deformation can be achieved without very large forces and without departing from the elastic nature of the deformation. In the solution shown in fig. 6, the rim device 4A comprises a plurality of rim members 4, which rim members 4 together define a circular outer rim 5. In this case, a plurality of rim members 4 together form an array of rim members 4, each rim member 4 defining a segment of a circular outer rim 5 for transferring traction to the cords 2. In the embodiment of fig. 6, the rim member 4 need not be deformable.

For adjusting the diameter of the rims 5 of the adjustable rim sets 4A, the drive sheave 1 further comprises adjusting means 10, 20, 30, 40, 50, 60 for individually adjusting the diameter of the circular outer rim 5 of each adjustable rim set 4A.

The adjusting device 10, 20, 30, 40, 50, 60 is electrically controllable. Particularly preferably, the adjusting means are electrically controllable by an elevator controller configured to automatically control the motor to rotate the drive sheave of the mechanism. For this purpose, the adjusting device 10, 20, 30, 40, 50, 60 comprises one or more input devices i for electrical control signals. An elevator controller 100 is shown in fig. 3 and 10.

Fig. 7-9 show a preferred alternative embodiment for achieving diameter adjustment by means of wedging. In these embodiments, the adjustment device 10, 20, 30 comprises: wedging means 11, 21, 31 which can be actuated to wedge the rim member 4 of the adjustable rim set 4A (i.e. the above-mentioned rim member 4 or rim members 4, which individually or collectively define the circular outer rim 5) radially outwards from the rotation axis X and release this wedging; and an actuator 12, 22, 32 for actuating the wedging means 11, 21, 31. The drive mechanism M preferably comprises such components for each adjustable rim set 4A.

In the embodiment of fig. 7-9, the wedging device 11, 21, 31 comprises a wedging member 11, 21, 31 disposed in a radial direction between the axis of rotation X and the rim member 4 of the adjustable rim device 4A, the wedging member 11, 21, 31 being movable forward F relative to the rim member 4 to wedge the rim member 4 radially outward from the axis of rotation X and rearward B relative to the rim member 4 to release the wedge and clear the rim member 4 for radial movement of the rim member 4 toward the axis of rotation X, and the actuator 12, 22, 32 is arranged to actuate movement of the wedging member 11, 21, 31 in the forward-rearward direction F, B. These embodiments differ in that in the embodiment of fig. 7 and 8 the back-and-forth movement is oriented parallel to the direction of the axis of rotation X, whereas in the embodiment of fig. 9 the back-and-forth movement is oriented in a tangential direction to the axis of rotation X.

In the embodiment of fig. 7-9, the wedging member 11, 21, 31 has a radially (i.e. in the radial direction of the rotation axis X) inclined outer side, in particular has a first end and a second end displaced in the direction of the rotation axis X, the first and second ends being at different distances from the rotation axis X, the wedging member 11, 21, 31 being movable against a radially (i.e. in the radial direction of the rotation axis X) inner side of the rim member 4 to wedge the rim member 4 radially outwards from the rotation axis X.

In the embodiment of fig. 7 and 8a-8b, the rim member 4 has a radially inner portion facing the inclined radially outer portion of the wedging member 11, 21, 31 and is also inclined, in particular having a first end and a second end displaced in the direction of the rotation axis X, the first and second ends being at different distances from the rotation axis X.

The wedging member 11, 21, 31 is preferably annular and surrounds the axis of rotation X. Thus, assuming a single rim member or an array of rim members (see fig. 5 and 6), the wedging members can be used to wedge into the rim members 4 evenly and in a structurally simple manner.

In the embodiment of fig. 7 and 8a-8b, the wedging members 11, 21 have a tapered radial outer side. Similarly, the rim members 4 have a tapered radially inner side, or as described in connection with fig. 6, the radially inner sides of the array rim members 4 collectively define a tapered shape.

In the embodiment of fig. 7 and 8a-8b, the wedging may be caused by at least one wedging member 11, 21. Preferably, however, there are two wedging members 11, 21 acting on the same rim member 4. Moreover, it is preferably implemented such that the two wedging members 11, 21 have a forward F direction and a backward B direction opposite to each other. This contributes to the compactness of the overall structure. Furthermore, this provides at least a portion of the forces that cancel each other, thereby more simply providing a reaction force for wedging. In the embodiment of fig. 7 and 8a-8b, the wedge is configured to bring the two wedging members 11, 21 closer to each other and to be released by further separating the two wedging members 11, 21.

In the embodiment of fig. 7, the actuator 12 is a motor. Most preferably, the motor is an electric motor and the rotation, preferably the rotational speed and/or the rotational direction, of the motor 12 is electrically controllable.

The actuator 12, here a motor, is connected with the wedging device 11, in particular with the wedging member 11 of the wedging device, via at least one driving member 13. Rotation of the motor 12 in one direction is configured to move the wedging member 11 forward F in the direction of the rotation axis X, and rotation of the motor in the other direction (i.e. the direction opposite to the above-mentioned one direction) is configured to move the wedging member 11 backward B in the direction of the rotation axis X.

In the embodiment of fig. 7, the actuator 12, i.e. the motor 12, may move the wedging member 11 by means of a screw. For this purpose, the above-mentioned at least one driving member comprises a screw member 13, the screw member 13 being oriented in a direction parallel to the rotation axis X, and the wedging member 11 comprises an internal thread which meshes with an external thread of the screw member 13.

In the embodiment of fig. 7, the adjustment is achieved with two wedging members 11. In particular, the adjustment device 10 comprises two wedging members 11, the wedging members 11 being movable by the actuator 12 simultaneously towards each other in the direction of the rotation axis X, simultaneously wedging the rim member 4 radially outwards from the rotation axis X, and/or simultaneously away from each other in the direction of the rotation axis X to release the wedging and to give way to the rim member 4 to move it radially towards the rotation axis X.

The inclined outer side portion of each wedge member 11 faces the inclined radially inner side of the rim member 4 of the adjustable rim set 4A, and the inclined portions of the rim member 4 under the action of the two wedge members 11 are mirror-shaped with respect to a rotation plane p of the drive sheave body 3 (a plane p perpendicular to the axis X in the drawing).

In the embodiment shown, the two wedging members 11 share a drive member, in the case shown a screw member 13 extending through the wedging member 11, and each of the two wedging members 11 comprises an internal thread which meshes with the 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 rotation plane p of the drive sheave body 3. Thus, by rotation of the screw member 13 in one rotational direction, the two wedging members 11 move towards each other (moving in direction F, respectively), and by rotation of the screw member 13 in the other rotational direction, the two wedging members 11 move away from each other (moving in direction B, respectively). For example, the actuator 12 may be immovably mounted on the drive sheave body 3. However, the actuator 12 may alternatively be immovably mounted on the wedging member 11 (either of the figures), in which case the screw member 13 need not be in threaded engagement with both wedging members 11.

In the embodiment of fig. 7, the drive sheave 1 further comprises blocking means 14a, 14b for blocking the 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, the blocking member 14a being placed in a groove formed between the wedging member 11 and the rim member 4. The recess 14b is larger than the stop member 14a to allow relative movement of the wedge member 11 and the rim member 4 in the direction of the axis of rotation x in the wedge. Therefore, the blocking member 14a does not block the relative movement of the wedge member 11 and the rim member 4 in the direction of the rotation axis x in this wedge.

In the embodiment shown in fig. 8a and 8b, the rim member 4 of the adjustable rim set 4A has a threaded radially inner side that is inclined and engages with a threaded inclined radially outer side of the wedging member 21, and the wedging member 21 is rotatable relative to the rim member 4 by the actuator 22.

In the embodiment shown in fig. 8a and 8b, the actuator 22 is a hydraulic cylinder connected to the wedging device 21, in particular to the wedging member 21 of the wedging device 21. One of the expansion and contraction of the hydraulic cylinder 22 is configured to rotate the wedge member 21 in one rotational direction relative to the rim member 4 and to move the wedge member forward F in the direction of the rotation axis X under the guidance of the threaded engagement between the rim member 4 and the wedge member 21, thereby wedging the rim member 4 radially outward from the rotation axis X. The other of the expansion and contraction of the hydraulic cylinder 22 is configured to rotate the wedging member 21 in the other rotational direction relative to the rim member 4 and to move the wedging member 21 rearwardly B in the direction of the axis of rotation X guided by the threaded engagement between the rim member 4 and the wedging member, thereby releasing the wedge and giving way to the rim member 4 to move it radially towards the axis of rotation X. The relative rotation between the wedging member 21 and the rim member 4 may alternatively be achieved with a motor, such as the electric motor described in connection with figure 7.

In the embodiment of fig. 8a-8b, the actuator 22, i.e. the hydraulic cylinder 22, can move the wedging member 23 by means of a screw. In the embodiment shown in fig. 8a and 8b, the adjustment is achieved with two wedging members 21. In particular, the adjustment device 20 comprises two wedging members 21, which wedging members 21 can be rotated by an actuator 22 with respect to the rim member 4 and can be moved simultaneously towards each other in the direction of the rotation axis X and simultaneously wedge the rim member 4 radially outwards from the rotation axis X and/or simultaneously moved away from each other to simultaneously release the wedge and give way to the rim member 4 to move it radially towards the rotation axis X. The radially outer portion of the inclined threads of each wedge member 21 then engages the radially inner portion of the inclined threads of the rim member 4 of the adjustable rim set 4A. Subsequently, the two wedging members 21 (including the thread and the inclined shape) and the parts of the rim member 4 (including the thread and the inclined shape of the rim member) in contact therewith take a mirror surface shape with respect to the rotation plane of the driving sheave body 3 (the plane p in fig. 8 perpendicular to the axis X), which is also parallel to the rotation plane of the wedging members 21. Thus, when the two wedging members 21 are rotated together in one direction relative to the rim member 4, the two wedging members 12 are simultaneously screwed along the threads of the rim member 4 to move toward each other (move in the direction F, respectively), and when the two wedging members 21 are rotated together in the other direction relative to the rim member 4, the two wedging members 12 are screwed along the threads of the rim member 4 to move away from each other (move in the direction B, respectively). The actuator 22 is preferably immovably or at least substantially immovably mounted on the drive sheave body 3.

In the embodiment shown in fig. 8a and 8b, the drive sheave 1 further comprises a synchronization device 24a, preferably at least a synchronization member 24a, for synchronizing the rotation of the two wedging members 21. The synchronization means are arranged to allow relative movement of the two wedging members 21 in the direction of the rotation axis X and to prevent relative rotation between the wedging members 21. The synchronization member 24a may be, for example, a rod facing parallel to the rotation axis X, one end of which extends into a hole formed in one of the two wedging members 21 and the other end of which extends into a hole formed in the other of the two wedging members 21, wherein the hole is also oriented parallel to the rotation axis X.

In the embodiment of fig. 9, the wedging member 31 has a plurality of radially (i.e. in the radial direction of the rotation axis X) outer sides which are inclined, in particular having a first end and a second end displaced in the tangential direction of the rotation axis X, at different distances from the rotation axis X, the wedging member 31 being movable against a radially (i.e. in the radial direction of the rotation axis X) inner side of the rim member 4 to wedge the rim member 4 radially outwards from the rotation axis X.

In fig. 9, a structure consistent with fig. 5 is shown. The seams between successive rim members 4 are drawn in dashed lines to illustrate a configuration consistent with fig. 6.

The individual rim members 4 or the array of rim members 4 of the above-described adjustable rim device 4A collectively (as described in connection with fig. 6) comprise a plurality of radially inner sides which face the inclined radially outer sides of the wedging members 31 and which are also inclined, in particular having first and second ends displaced in a tangential direction of the rotation axis X, the first and second ends being at different distances from the rotation axis X.

The wedging member 31 is movable forward F in a direction tangential to the axis of rotation X relative to the rim member 4 or array rim member 4 to wedge the rim member 4 radially outwardly from the axis of rotation X and rearward B to release the wedge and give way for the rim member 4 to move radially toward the axis of rotation X, and the actuator 32 is arranged to actuate movement of the wedging member 31 in the forward and rearward direction F, B. In a preferred embodiment, actuator 32 is a hydraulic cylinder connected to wedging member 31 and the driving sheave body. The above-mentioned rim members 4 or array rim members 4 are completely or at least substantially non-rotatable around the rotation axis X relative to the drive sheave body 3, whereby relative movement can be ensured.

One of the expansion and contraction of the hydraulic cylinder 32 is configured to rotate the wedge member 31 in one rotational direction relative to each rim member 4, and to move the wedge member 31 forward F in a tangential direction of the rotation axis X, thereby wedging each rim member 4 radially outward from the rotation axis X. The other of the expansion and contraction of the hydraulic cylinder 32 is configured to rotate the wedge member 31 in the other rotational direction relative to each rim member 4, and move the wedge member 31 rearward B in the direction of the rotation axis X, thereby releasing the wedge and giving way to each rim member 4 to move it radially toward the rotation axis X. The relative rotation between the wedging member 31 and the rim member 4 or the array rim member 4 about the axis of rotation may alternatively be achieved with a motor, such as the electric motor described in connection with figure 7.

Figure 10 shows a preferred alternative embodiment for diameter adjustment by means of screws. In this embodiment, the adjustment device 40 comprises (preferably for each adjustable rim device 4A) a screwing device 41a-41d which can be actuated to push the rim members 4 of the adjustable rim device 4A (i.e. the single rim member 4 or the plurality of rim members 4 which define or collectively define the circular outer rim 5 of the adjustable rim device 4A as described above) radially outwards from the axis of rotation X. The screw means 41a-41d that can be actuated can be further actuated to release the pushing. The adjustment device 40 further comprises an actuator 42 for actuating the screwing devices 41a-41 d.

In the drive mechanism M of fig. 10, the actuator 42 is preferably an electric motor, and the rotation, preferably the rotational speed and/or the rotational direction, of the motor 42 is electrically controllable. The actuator 42 is shown in dashed lines in fig. 10. The actuator 42 is preferably fixedly mounted on the drive sheave body 3.

In the drive mechanism M of fig. 10, the screwing means 41a-41d comprise a screw 41c rotatable by an actuator 42. Each screw 41c can be rotated in both directions by the actuator 42 about an axis a extending in a radial direction of the rotation axis X. Only the axis a of one screw 41c is shown. The rotation axis of the motor 42 is parallel to the rotation axis X. The actuator 42 is arranged to rotate each screw 41c via a bevel gear mechanism 41a, 41 b.

Each screw 41 is arranged to urge the rim member 4 radially outwardly from the axis of rotation X when rotated by the actuator in one rotational direction, and to release the urging and give way to the rim member 4 to move it radially rearwardly towards the axis of rotation X when rotated by the actuator in the other rotational direction.

The actuator 42 is arranged to rotate each screw 41c in one rotational direction to urge the rim member 4 radially outwardly from the rotational axis X and in the other rotational direction to release the urging and to give way to the rim member 4 to move it radially back towards the rotational axis X, within a threaded opening 41d provided on the drive sheave body 3, or alternatively within an element fixedly mounted on the drive sheave body. The releasing and yielding may also include pulling the rim member 4 to move it radially back towards the axis of rotation X.

Fig. 11 shows a preferred alternative embodiment for achieving diameter adjustment by hydraulically deforming the rim members of each adjustable rim set 4A. In this embodiment, each rim member 4 (i.e. the above-mentioned single rim member 4 or the above-mentioned plurality of rim members 4 defining or jointly defining the circular outer rim 5 of the adjustable rim device 4A) comprises a hydraulic chamber 51 containing a hydraulic fluid 54, and a radially outer wall 4 ' of the hydraulic chamber, which radially outer wall 4 ' borders the hydraulic chamber 51, in particular on the radially outer side, the shape of the radially outer wall 4 ' being elastically deformable. The adjustment device 50 comprises a pressure adjustment system 52, 53 for adjusting, in particular increasing or decreasing, the fluid pressure in the hydraulic chamber 51 of the rim member 4. The pressure regulating system 52, 53 may, for example, comprise a pressurizing device 52 (schematically shown), such as a hydraulic pump or a hydraulic cylinder, which is connected with each hydraulic chamber 51 of the adjustable rim set 4A by at least one fluid channel 53. The pressure regulating systems 52, 53 may also include valves for controlling fluid flow and/or fluid pressure.

The pressure regulating system 52, 53 may be operated to increase the fluid pressure in the hydraulic chamber 51, so that the radially outer wall 4 'bulges radially outwards from the rotation axis X, and to release this pressure, in particular so that the radially outer wall 4' contracts radially backwards from the bulged state towards the rotation axis X.

Figure 12 shows another preferred alternative embodiment for achieving diameter adjustment by hydraulically deforming the rim members 4 of each adjustable rim set 4A. In this embodiment, each rim member 4 (i.e. the single rim member 4 or a plurality of rim members 4 described above which define or collectively define the circular outer rim 5 of the adjustable rim apparatus 4A) comprises: a plurality of hydraulic chambers 61 containing hydraulic fluid 64, and a radially outer wall 4 ' of the hydraulic chambers, the radially outer wall 4 ' in particular bordering on the radially outer side the hydraulic chambers 61, the radially outer wall 4 ' being elastically deformable in shape; and pressure adjusting systems 62, 63 for adjusting the fluid pressure in the hydraulic chamber 61 of the rim member 4 of the adjustable rim set 4A. The pressure regulation system 62, 63 may, for example, comprise a pressurizing device 62 (schematically shown), such as a hydraulic pump or a hydraulic cylinder, which is connected with each hydraulic chamber 61 of the adjustable rim set 4A by at least one fluid channel 63. The pressure regulating systems 62, 63 may also include valves for controlling fluid flow and/or fluid pressure.

The pressure regulating systems 62, 63 are operable to increase the fluid pressure within each hydraulic chamber 61 of the rim member 4, so that the radially outer wall 4 'bulges radially outward from the rotation axis X, and to release the pressure, in particular so that the radially outer wall 4' contracts radially rearward from the bulged state towards the rotation axis X.

As shown in fig. 12, the plurality of hydraulic chambers 61 of the rim member 4 are preferably located beside each other in the direction of the rotation axis X.

The fluid pressures in the hydraulic chambers 61 of the rim members 4 are preferably adjustable to be different from each other.

To facilitate adjusting the fluid pressures within the hydraulic chambers 61 of the rim member 4 to be different from each other, in a preferred embodiment, the fluid pressures within the plurality of hydraulic chambers 61 may be individually adjusted by the pressure adjustment systems 62, 63, i.e., the pressure adjustment systems 62, 63 may adjust, in particular increase or decrease, the fluid pressures within the respective hydraulic chambers 61 of the rim member 4 without changing the pressures within the other hydraulic chambers of the rim member 4.

To facilitate adjusting the fluid pressures within the hydraulic chambers 61 of the rim member 4 to be different from each other, in a preferred embodiment, the pressure adjustment systems 62, 63 preferably include fluid passages 63 respectively connected to the hydraulic chambers 61 of the rim member 4 for achieving adjustment of the fluid pressures within the hydraulic chambers 61 of the rim member 4 to be different from each other.

The above-described adjustment of the fluid pressures in the hydraulic chambers 61 of the rim member 4 to be different from each other provides an additional advantage in that the profile of the rim member 4 can be adjusted to control the position of the rope 2 in the direction of the rotation axis X. The amount of curvature of the profile of the rim member 4 by which the cords can be guided in the direction of the axis of rotation X towards the peak of the convex profile can be increased or decreased. The asymmetry of the profile of the rim member 4 with respect to the plane of rotation p of the drive sheave body 3, by which asymmetry the rope can be guided in the direction of the axis of rotation X towards a desired position, can also be increased or decreased.

In the embodiment of fig. 11 and 12, the drive sheave 1 may have a hydraulic pressurization device 52, 62 for each adjustable rim device 4A, but this is not necessary, since the hydraulic pressure may be shared to achieve the adjustment of a plurality of adjustable rim devices 4A, in particular since the fluid may be pressurized by a single pressurization device (e.g. a pump or a hydraulic cylinder) and connected to a plurality of hydraulic chambers, and a control valve is used between the pressurization device and each hydraulic chamber, which is adjustable to reduce the fluid pressure individually.

As mentioned above, the diameter of the rims 5 of one or more rim sets 4A can be individually adjusted to increase or decrease the turning radius of the rope 2 passing around the rim 5 in question. Most preferably, the diameter of the rims 5 of more than one (all or all but one) of the rim devices 4A can be individually adjusted to enlarge or reduce the turning radius of the rope 2 passing around the rim 5. The drive mechanism M may, for example, comprise 2, 3, 4, 5, 6, 7, 8, 9 or 10 rim sets 4A and the diameter of the circular outer rim 5 of all or but one of the rim sets 4A may be individually adjusted to enlarge or reduce the turning radius of the rope 2 passing around the circular outer rim 5 in question.

In a preferred embodiment, the motor m is connected to the drive sheave body 3, preferably directly or via a transmission, so that the motor m can rotate the drive sheave body 3. The drive sheave body 3 is preferably directly fixed to or integrally formed with the rotor r of the motor m. Alternatively, a force transmission means, such as a gear, may be provided between the motor m and the drive sheave body 3. The adjusting device 10, 20, 30, 40, 50, 60 is preferably mounted on the drive sheave body 3 so as to be rotatable together with the drive sheave body 3 about the axis of rotation X.

Generally, releasing (i.e., releasing the wedging and/or urging) and giving way to the rim member 4 to move radially toward the axis of rotation X may also include pulling the rim member 4 to move radially back toward the axis of rotation X. This can be achieved simply by mechanically connecting the components to each other radially immovably or at least substantially immovably. This may be achieved, for example, by connecting the wedging means 11, 21, 31 (e.g. the wedging members 11, 21, 31) to the rim member 4 radially immovably or at least substantially immovably, or by connecting the screwing means (e.g. the screw 41c) to the rim member 4 radially immovably or at least substantially immovably.

The elevator preferably comprises a tension sensing means s for sensing the individual tension of one or more ropes 2, and the elevator is configured to adjust the diameter of the circular outer rim 5 of at least one adjustable rim means 4A by means of the adjusting means 10, 20, 30, 40, 50, 60 based on the sensed individual tension 2. As shown in fig. 3, the tension sensing means may comprise a force sensor disposed between the elevator car c and one end of the rope 2 fixed to the elevator car c for sensing the individual tension of the rope 2, and/or a force sensor disposed between the counterweight and one end of the rope fixed to the counterweight for sensing the individual tension of the rope 2. In the 2:1 solution, the force sensor is preferably located at one end of the rope fixed to a stationary fixed base on the c-side of the elevator car (e.g. a stationary structure of the building) to sense the individual tension of the rope 2 and/or at one end of the rope fixed to a stationary fixed base on the counterweight side (e.g. a stationary structure of the building) to sense the individual tension of the rope 2. Of course, there are many alternative ways of measuring the individual rope tensions.

Preferably, the elevator is more particularly arranged to sense the individual tension of one or more ropes 2, compare the sensed individual tension with one or more reference tensions, and adjust the diameter of the circular outer rim 5 of at least one adjustable rim device 4A by means of the adjusting device 10, 20, 30, 40, 50, 60 based on the sensed individual tension 2, in particular such that the difference between the measured tension and the reference tension is reduced.

The one or more reference tensions may comprise, for example, a preset tension or a measured individual tension mean tension of a plurality of ropes, or a measured individual tension of one other rope of the elevator.

As mentioned above, in the solution shown in figure 5, the adjustable rim set 4A comprises a single rim member 4 defining a circular outer rim 5. In this case, one rim member 4 defining the circular outer rim 5 may be deformed to have different diameters, which may be achieved by an elastic material and/or structure. The deformability of the circular outer rim 5 with different diameters can be structurally promoted, for example, by providing the rim member of the adjustable rim set 4A with a plurality of cavities cv, as shown in fig. 14A and 14 b. In these figures, it is preferred, although not necessary for other features to be present, that the rim member 4 includes a cavity cv. In the case shown, the rim member 4 comprises a plurality of cavities cv arranged side by side in the direction of rotation X and distributed along the tangential direction of the rim 5. In the case shown, the cavity is an elongated cavity and is oriented in the tangential direction of the rim 5.

It should be understood that the above description and accompanying drawings are only intended to teach the best way known to the inventors to make and use the invention. It is obvious to a person skilled in the art that the inventive concept can be implemented in various ways. Thus, as may be recognized by those of ordinary skill in the pertinent art based on the teachings herein, the above-described embodiments of the present invention may be modified or varied without departing from the invention. 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.