Braking device and car arrangement for an elevator system, and elevator system

Abstract

The invention also relates to a braking device (24) comprising a load measuring device (33) for an elevator system (10). The elevator system (10) has an elevator shaft (12), an elevator car (14) which is movably arranged in the elevator shaft (12), and at least one guide rail (16) which is fixedly arranged in the elevator shaft (12) and which is designed to guide the elevator car (14) when the elevator car is moved. The braking device (24) has: a car mount (26) for fastening the braking device (24) to the elevator car (14); a brake body (28) which is mechanically coupled to the car mount (26); a brake unit (30) which is arranged on the brake body (28) and which is designed to be brought in physical contact with the guide rail (16) when the brake device (24) is arranged on the elevator car (14) as intended and when the elevator system (10) is braked, and to generate such a strong frictional force between the guide rail (16) and the brake unit (30) that the brake unit (30) and the elevator car (14) coupled to the brake unit are braked; a load-measuring pin (32), by means of which the car mount (26) is mechanically coupled to the brake body (28) and which has a strain gauge (70), the load-measuring pin (32) and the strain gauge (70) being arranged such that a force which acts between the car mount (26) and the guide element (60) in a direction parallel to the guide rail (16) during the braking process causes deformation of the load-measuring pin (32) and thus a strain on the strain gauge (70); and an electronic component (80) which is electrically coupled to the strain gauge (70) and which is designed to generate an output signal depending on the strain on the strain gauge (70), the output signal being representative of the force, and a load which is currently being conveyed by the elevator car (14) being measurable by means of the output signal so that the load-measuring pin (32) and the electronic component (80) can be used as a load-measuring device (33).

Description

[0001] Braking device and cabin arrangement for an elevator system, and elevator system

[0002] Description

[0003] The present invention relates to a braking device for an elevator system, a car arrangement for the elevator system having the braking device, and the elevator system with the car arrangement and the braking device.

[0004] Such an elevator system typically comprises an elevator shaft extending through a building with multiple floors. An elevator car is located in the elevator shaft and can be moved vertically within the elevator shaft between different height levels, for example, between floors. The elevator car can be moved using a drive mechanism that is mechanically coupled to the elevator car by means of a support member and is designed to move the support member and thereby move the elevator car. The support member can comprise, for example, a rope or a belt. Furthermore, two or more support members can be used to move the elevator car. The drive mechanism can comprise, for example, an electric motor whose motor shaft is mechanically coupled to a traction sheave, over which the support member is guided.

[0005] The elevator car can be guided during its movement by one or more guide rails that are fixedly arranged in the elevator shaft, for example, on the shaft walls of the elevator shaft. A vertical movement of the elevator car can be slowed down by a service brake, for example, to bring the elevator car to a stop at one of the floors after it has been moved. Such service brakes are known and can traditionally be arranged on the drive mechanism and, to slow down the elevator car, brake the rotation of a motor shaft of the drive mechanism. However, service brakes are now also known that are arranged directly on the elevator car and are coupled to the fixed guide rails during a braking operation so that the elevator car is slowed down.When people enter or exit an elevator car stopped at a floor, the load currently being carried by the elevator car changes. The resulting load change can lead to a change in the length of the support element due to elastic deformation of the support element. Accordingly, the position of the elevator car relative to the floor may change slightly during the stop at that floor due to the load change. To prevent a step from forming between a floor of the elevator car and the floor of the corresponding floor due to the change in position, it is known to compensate for a change in the position of the elevator car using a so-called "re-leveling" system. In this process, the drive device specifically moves the support elements holding the elevator car in such a way that the change in position of the elevator car is counteracted.However, implementing such a leveling measure requires complex measures.

[0006] Alternatively, it is known to provide a brake directly on the elevator car, for example, the service brake, which can be used to hold the elevator car in position during a stop at the corresponding floor. However, the load change during the stop can cause a sudden change in the position of the car when the brake is subsequently released due to the changed car load. This can impair ride comfort and / or negatively impact the service life of the suspension elements and / or the drive system.

[0007] For this reason, it is known to determine the load change by means of a load measuring device and, depending on the determined load change, to pre-tension the support element in such a way that there is no sudden change in the position of the cabin when the brake is subsequently released.

[0008] WO 2023 / 117773 A1 describes a braking device for braking a movable elevator car of an elevator system and for measuring load changes induced in the elevator car. The braking device comprises: two brakes for braking the elevator car relative to a stationary component of the elevator system; a brake holding arrangement for holding the brake to the elevator car; a load measuring device with a force transmission element for measuring a force acting on the force transmission element; and a load measuring device holding arrangement for holding the load measuring device to the elevator car. The load measuring device comprises several components that are mechanically connected to one another and that move relative to one another when the force is detected.

[0009] There may be a need, among other things, for a braking device with a load measuring device in which the load measuring device has very few components, is of simple design, is inexpensive to manufacture and / or requires little maintenance.

[0010] Such a need can be met by the subject matter according to one of the independent claims. Advantageous embodiments are defined in the dependent claims and the following description.

[0011] A first aspect of the invention relates to a braking device with a load-measuring device for an elevator system. The elevator system comprises an elevator shaft, an elevator car that is arranged displaceably in the elevator shaft, and at least one guide rail that is fixedly arranged in the elevator shaft and is designed to guide the elevator car during its displacement. The braking device comprises: a car mount for attaching the braking device to the elevator car; a brake body that is mechanically coupled to the car mount;a brake unit arranged on the brake body and designed to be brought into physical contact with the guide rail when the braking device is arranged as intended on the elevator car and during a braking operation of the elevator system, and to generate such a high frictional force between the guide rail and the brake unit that the brake unit and the elevator car coupled to the brake unit are braked; a load measuring pin, by means of which the car mount is mechanically coupled to the brake body and which has a strain gauge, wherein the load measuring pin and the strain gauge are arranged such that a force acting between the car mount and the guide element in a direction parallel to the guide rail during the braking operation causes a bending of the load measuring pin and thus an elongation of the strain gauge;and an electronic component that is electrically coupled to the strain gauge and that is designed to generate an output signal depending on the strain of the strain gauge, wherein the output signal is representative of the force and wherein a load located in the elevator car can be determined depending on the force, so that the load measuring bolt and the electronic component can be used as a load measuring device.;

[0012] A second aspect of the invention relates to a car assembly for the elevator system with the elevator shaft. The car assembly comprises the elevator car and at least one braking device as described above and below, which is arranged on the elevator car.

[0013] A third aspect of the invention relates to the elevator system comprising the elevator shaft and the car arrangement.

[0014] The strain gauge is designed such that its electrical resistance changes when it is stretched. The electronic component is designed to determine, in particular to detect, the electrical resistance of the strain gauge. For example, the electronic component can be designed to apply a voltage to the strain gauge and detect a current that flows through the strain gauge due to the applied voltage. The electronic component can, for example, have or be a full bridge. The output signal of the electronic component is representative of the electrical resistance of the strain gauge, thus of the extent of the strain gauge's stretch and thus of the force acting on the load measuring bolt due to the braking process.To apply the voltage, the electronic component can be connected to an energy source, such as a battery or a power grid.

[0015] The electronic component can be communicatively coupled to an evaluation unit, wherein the evaluation unit is configured to determine the force acting on the load-measuring pin due to the braking process based on the output signal of the electronic component. The evaluation unit can be a component of the braking device. Alternatively, the evaluation unit can be a component of an elevator control system of the elevator system.

[0016] The fact that the load measuring pin and the strain gauge are arranged in such a way that a force acting during the braking process between the car mount and the guide element in a direction parallel to the guide rail causes a bending of the load measuring pin and thus an extension of the strain gauge can, in the most general case, mean that, when the braking device is arranged as intended, a longitudinal axis of the load measuring pin or the strain gauge extends at least partially in a horizontal direction. Ideally, this can mean that the longitudinal axis and the strain gauge extend in a horizontal direction and thus perpendicular to the force acting in the vertical direction. In this case, the bending of the load measuring pin and the resulting extension of the strain gauge are maximum for a given force, so that a very good signal-to-noise ratio can be achieved and the force can be determined very precisely.This can help determine the load currently being transported by the elevator car, especially its weight, with great precision. The load can include one, two, or more people and / or one, two, or more items of goods.

[0017] In the intended arrangement of the braking device, the car mount is arranged on the elevator car in the elevator shaft in such a way that the frictional force between the braking unit and the guide rail can be generated by means of the braking unit. The intended arrangement can also refer to the orientation of the elevator car. In particular, in the intended arrangement of the elevator car, a floor of the elevator car is at the bottom and a roof of the elevator car is at the top. Furthermore, in the intended arrangement, the braking device can be arranged below the elevator car. The intended arrangement of the braking device can also refer to an orientation of the braking device, wherein the braking device is arranged as intended, for example, when the load measuring pin, in particular its longitudinal axis, extends in a horizontal direction.

[0018] The brake unit can, for example, be a mechanical and / or hydraulic brake. The brake unit can, for example, have one, two or more pairs of brake shoes. When the braking device is arranged as intended, the guide rail can run between the brake shoes. Optionally, the braking device can have brake pads arranged on the brake shoes so that the brake pads face the guide rail. The brake shoes and, if applicable, the brake pads can be designed and arranged such that, outside of the braking process, there is only very little or no physical contact between the brake shoes or brake pads and the guide rail, and that during the braking process the brake shoes or brake pads touch the guide rail and thereby generate the frictional force required for the braking process.The brake unit can, for example, have a spring, particularly a C-shaped spring, for each pair of brake shoes. The brake shoes can be arranged at the mutually facing ends of the corresponding "C." The spring can be arranged on the brake body and preloaded such that the spring presses the brake shoes toward the guide rail. The brake unit can, for example, have a mechanically and / or hydraulically actuated piston designed to press the brake shoes away from the guide rail against the spring force of the spring.In this way, it can be ensured that in the event of a power failure and / or a malfunction of the hydraulics, where the lifting piston cannot perform a stroke and / or exert any force against the spring, the elevator car cannot fall uncontrollably, as the brake shoes are then pressed towards the corresponding guide rail due to the spring force of the spring and the braking process is initiated automatically.

[0019] The braking device can also be referred to as the service brake of the elevator system. Service brakes are often installed on drive devices, especially motors, for moving the elevator car. Installing the braking device and thus the service brake on the elevator car allows the load currently being transported by the elevator car to be determined using the service brake.

[0020] The car arrangement may comprise two or more braking devices. The braking devices may be arranged on opposite sides of the elevator car and interact with opposing guide rails for braking. The braking devices may be arranged on the same side of the elevator car, for example, one above the other, to interact with the same guide rail, or the braking devices may be arranged on the same side of the elevator car, for example, side by side, to interact with two parallel guide rails. Furthermore, these alternatives may be combined with one another, for example, with multiple braking devices arranged at the same height, for example, side by side and / or around the elevator car, and multiple braking devices arranged one above the other.

[0021] According to one embodiment, the load-measuring pin has a longitudinal axis, the load-measuring pin has a cavity that extends parallel to the longitudinal axis at least partially through the load-measuring pin, and the strain gauge is arranged in the cavity. This makes it possible to protect the strain gauge from external influences. In particular, it can prevent the strain gauge from being damaged by a bearing in which the load-measuring pin is mounted. The load-measuring pin can, for example, be substantially rotationally symmetrical and / or cylindrical. In this case, the longitudinal axis can correspond to an axis of symmetry of the load-measuring pin.

[0022] According to one embodiment, the load measuring pin is arranged so that its longitudinal axis extends horizontally. This can help to generate the greatest possible strain of the strain gauge for a given force and thus the strongest and / or most precise output signal from the electronic component, which can contribute to particularly precise load determination.

[0023] According to one embodiment, the brake body has a first load-measuring pin receptacle in which at least one axial section of the load-measuring pin, i.e., a section of the load-measuring pin that extends in the axial direction of the load-measuring pin, is arranged. The first load-measuring pin receptacle is configured such that, when the braking device is arranged as intended, the load-measuring pin is positively secured in the first load-measuring pin receptacle in the vertical direction and is displaceable in the horizontal direction relative to the first load-measuring pin receptacle. The load-measuring pin receptacle can serve as a bearing for the load-measuring pin. The load-measuring pin receptacle can, for example, have a first eyelet, wherein, when the braking device is arranged as intended, a central axis of the first eyelet runs horizontally.The first eyelet may be formed with a clearance fit to the load measuring pin so that the load measuring pin can be arranged in the first eyelet and can be rotated in the first eyelet relative to the first eyelet.

[0024] The fact that the load pin is positively secured vertically in the first load pin holder contributes to the secure vertical coupling of the cab mount to the brake body, even when a high vertical force acts on the cab mount and / or the brake body. This can also contribute to precise load determination.

[0025] The fact that the load-measuring pin is arranged in the first load-measuring pin receptacle so that it can be displaced horizontally relative to the first load-measuring pin receptacle enables the elevator car to be moved horizontally relative to the braking device. For example, the load-measuring pin and the load-measuring pin receptacle can be configured such that the elevator car can be moved horizontally relative to the guide rail within a range of ± 10 mm, for example within a range of ± 5 mm, for example within a range of ± 2 mm.

[0026] According to one embodiment, the first load-measuring pin receptacle is designed such that the brake body can be rotated about the load-measuring pin relative to the cabin mount. For example, the longitudinal axis of the load-measuring pin can be a rotation axis about which the brake body can be rotated relative to the cabin mount.

[0027] According to one embodiment, the cabin mount has a second load-measuring pin receptacle in which at least one axial section of the load-measuring pin is arranged and which is designed such that, when the braking device is arranged as intended, the load-measuring pin is positively secured in the second load-measuring pin receptacle in the vertical direction and is displaceable in the horizontal direction relative to the second load-measuring pin receptacle. In this context, axial sections arranged in the second load-measuring pin receptacle can be referred to as first or second axial sections, and axial sections arranged in the first load-measuring pin receptacle can be referred to as third axial sections.The second load-measuring pin receptacle can, for example, have two second eyelets that are arranged opposite one another and concentrically to one another. The center axes of the second eyelets can run horizontally and parallel to one another, for example, lying one on top of the other. The second eyelets can be designed with a clearance fit with the load-measuring pin, so that the load-measuring pin can be arranged in the second eyelets and can be rotated in the second eyelets relative to the second eyelets. Alternatively, two first eyelets can be arranged on the brake body and / or only one second eyelet can be arranged on the cab mount.

[0028] According to one embodiment, the second load-measuring pin receptacle is designed such that the brake body can be rotated about the load-measuring pin relative to the cabin mount. For example, the longitudinal axis of the load-measuring pin can be a rotation axis about which the brake body can be rotated relative to the cabin mount.

[0029] According to one embodiment, the cage support is arranged at a first vertical end portion of the brake body when the braking device is arranged as intended, and the braking device further comprises a bearing assembly arranged at a second vertical end portion of the brake body, facing away from the first vertical end portion, which bearing assembly is fixed relative to the elevator cage and is movable vertically relative to the brake body. The fact that the bearing assembly is movable vertically relative to the brake body makes it possible to decouple the bearing assembly from the rest of the braking device, and in particular from the load measuring pin, with regard to the force acting on it due to the braking process, so that the force is essentially absorbed by the load measuring pin. This can contribute to a precise determination of the load that is currently to be transported by the elevator cage.

[0030] The bearing assembly can be coupled to the elevator car in such a way that it is arranged directly on the elevator car and touches the elevator car. If the elevator car is arranged in a safety frame, the bearing assembly can be arranged on the safety frame, can touch the safety frame, and can be mechanically coupled to the elevator car indirectly via the safety frame.

[0031] According to one embodiment, the bearing arrangement comprises a vertical piston arranged in a recess of the brake body, which extends vertically when the braking device is in its intended position, such that the vertical piston extends vertically and is movable vertically relative to the brake body. This makes it possible to decouple the bearing arrangement from the brake body with regard to force absorption and can contribute to ensuring that the largest possible proportion of the force, ideally the entire force acting on the braking device during braking, is absorbed by the load measuring pin and not by the bearing arrangement. This can contribute to the particularly precise determination of the load currently located in the elevator car.

[0032] According to one embodiment, a longitudinal section of the vertical piston is arranged in the recess, a third eyelet is formed at an elongated end of the longitudinal section, and the bearing arrangement comprises a pin that is guided through the third eyelet, is movable relative to the third eyelet, and is mechanically coupled to the elevator car outside the third eyelet. The third eyelet can, for example, be designed such that the pin is aligned horizontally when arranged in the third eyelet. The third eyelet and the pin can be designed with a clearance fit relative to one another, which can provide the mobility of the pin relative to the third eyelet. The fact that the pin is movable relative to the third eyelet can mean, for example, that the third eyelet can slide along the pin and / or the third eyelet can be rotated about the pin.For example, the pin in the third eyelet can be arranged so as to be displaceable in the horizontal direction relative to the third eyelet. This enables the elevator car to be moved horizontally relative to the braking device. For example, the pin and the third eyelet can be configured such that the elevator car can be moved horizontally relative to the guide rail within a range of ± 10 mm, for example within a range of ± 5 mm, for example within a range of ± 2 mm. The pin can be arranged on a brake bracket, which can represent at least part of the mechanical coupling between the bearing arrangement and the elevator car. The horizontal mobility of the eyelet relative to the pin enables a floating mounting of the brake body.

[0033] According to one embodiment, the braking device comprises a guide element which is arranged on the brake body and which is designed to guide the braking device on the guide rail when the elevator car is displaced.

[0034] According to one embodiment, the guide element comprises at least one pair of guide rollers rotatably mounted on the brake body, between which the guide rail is arranged when the braking device is arranged as intended. The guide rollers are designed and arranged such that the axes of rotation of the guide rollers are parallel to one another and that the rolling surfaces of the guide rollers face the guide rail and roll along it when the braking device is moved relative to the guide rail. The guide rollers can contribute to both precise and low-friction guidance of the braking device along the guide rail, the latter being particularly advantageous outside of the braking process.

[0035] According to one embodiment, the car assembly comprises a safety frame in which the elevator car is arranged, wherein the braking device is mechanically coupled to the safety frame. The braking device can thus be mechanically coupled to the elevator car and to the safety frame. In particular, the braking device can be mechanically coupled to the elevator car by means of the car mount and to the safety frame by means of the bearing assembly. In particular, the car mount can be arranged directly on the elevator car and / or contact it, and the bearing assembly can be arranged directly on the safety frame and / or contact it.

[0036] Embodiments of the invention are described below with reference to the accompanying drawings, wherein neither the drawings nor the description are to be construed as limiting the invention.

[0037] Fig. 1 shows a side sectional view through an elevator shaft of an elevator system in which an elevator car is arranged, according to an embodiment of the invention.

[0038] Fig. 2 shows a perspective view of a braking device of an elevator system according to an embodiment of the invention. Fig. 3 shows a partial perspective view of the braking device according to Figure 2.

[0039] Fig. 4 shows a partially sectioned side detail view of the braking device according to Figure 2.

[0040] The figures are merely schematic and not to scale. The same reference numerals designate identical or equivalent features in the various figures.

[0041] Fig. 1 shows a side sectional view through an elevator shaft 12 of an elevator installation 10, in which an elevator car 14 of the elevator installation 10 is arranged, according to an embodiment of the invention. The elevator installation 10 can be arranged in a building having two or more floors. The elevator installation 10 has a car arrangement 13. The car arrangement 13 has an elevator car 14 and at least one, for example two or more, braking devices 24. The elevator shaft 12 can extend over several of the floors. The building can have a shaft opening (not shown) on each of the floors through which the elevator car 14 is accessible from the corresponding floor when the elevator car 14 is located on the corresponding floor. Optionally, the car arrangement 13 can have a catch frame 15, in which the elevator car 14 is arranged and via which the elevator car 14 is coupled to the support means 18.

[0042] The elevator car 14 is arranged in the elevator shaft 12 in such a way that it can be displaced within the elevator shaft 12, in other words, can be moved from one height level to another within the elevator shaft 12. If the elevator shaft 12 extends vertically, the elevator car 14 is also displaced vertically. The height levels can, for example, correspond to the floors. In the event of maintenance work, the elevator car 14 can also be moved to height levels between the floors.

[0043] The elevator car 14 can be held by a support means 18, which is designed, for example, as a rope or belt. Optionally, two or more support means 18 can be arranged to hold the elevator car 14. The support means 18 can be mechanically coupled to a drive device 20 of the elevator system 10. The drive device 20 can, for example, have a motor, in particular an electric motor, and a traction sheave (not shown) that is mechanically coupled to a motor shaft (not shown) of the motor and that can be driven by the motor. The support means 18 can extend over the traction sheave, so that the support means 18 can be moved by the drive device 20, whereby the elevator car 14 can be displaced. The drive device 20 can be controlled by an elevator control system 22.

[0044] The elevator system 10 can have one, two, or more guide rails 16. The guide rails 16 can be arranged on the shaft walls of the elevator shaft 12 and extend over several of the floors. For example, one guide rail 16 can be arranged on each side of the elevator car 14. The guide rails 16 serve to guide the elevator car 14 during its movement, particularly on both sides.

[0045] The braking devices 24 can each be arranged on the outside of the elevator car 14. If the elevator system 10 has the safety frame 15 in which the elevator car 14 is arranged and via which the elevator car 14 is coupled to the support means 18, the braking devices 24 can be arranged on the safety frame 15 and / or on the elevator car 14. The braking devices 24 can be referred to individually or in conjunction as a service brake.

[0046] The braking devices 24 serve to decelerate a movement of the elevator car 14 due to the displacement of the elevator car 14, to stop it, and to keep it stationary during a stop at a desired position in the elevator shaft 12. In particular, after the elevator car 14 has been moved to the desired position by means of the drive device 20 and the support means 18, it can be temporarily secured to the guide rails 16 by means of braking units 30 arranged on the braking devices 24.

[0047] The car arrangement 13 can optionally have more than two braking devices 24. The braking devices 24 can be arranged on opposite sides of the elevator car 14 and interact with the opposing guide rails 16 for braking. Alternatively or additionally, the braking devices 24 can be arranged on the same side of the elevator car 14, for example, one above the other, to interact with the same guide rail 16 (not shown), or the braking devices 24 can be arranged on the same side of the elevator car 14, for example, next to each other, to interact with two parallel guide rails 16 (not shown). Furthermore, these alternatives can be combined with each other, for example, so that several braking devices 24 are arranged at the same height and several braking devices 24 are arranged one above the other (not shown).

[0048] Fig. 2 shows a perspective view of a braking device 24 of an elevator installation 10, according to an embodiment of the invention, and Fig. 3 shows a partial perspective view of the braking device according to Figure 2.

[0049] The elevator installation 10 can, for example, be the elevator installation 10 shown in Figure 1. The braking device 24 can be one of the braking devices 24 shown in Figure 1, wherein the two braking devices 24 can be of identical design. However, the braking device 24 can also be arranged in a different, in particular different, elevator installation 10 in order to brake, stop, and temporarily hold the elevator car 14 of the corresponding elevator installation 10 with the aid of corresponding guide rails 16. The elevator installation 10 can have a counterweight (not shown) that is coupled to the elevator car 14 via the support means 18. In Figure 1, the counterweight can be arranged behind the elevator car 14 so that it is concealed by the elevator car 14 in Figure 1 and thus not visible.

[0050] The braking device 24 comprises a car mount 26, a brake body 28, a brake unit 30, a load-measuring pin 32, and an electronic component 80. The car mount 26 is designed and arranged to fasten the braking device 24 to the elevator car 14. The car mount 26 can be arranged on the elevator car 14 by means of fastening elements 64, for example screws. The brake body 28 is mechanically coupled to the car mount. The car mount 26 is mechanically coupled to the brake body 28 by means of the load-measuring pin 32. The braking unit 30 is arranged on the brake body 38.The brake unit 30 is designed to be brought into physical contact with the corresponding guide rail 16 when the brake device 24 is arranged as intended on the elevator car 14 and during a braking operation of the elevator system 10 and to generate such a high frictional force between the guide rail 16 and the brake unit 30 that the brake unit 30, the brake body 28 coupled to the brake unit 30, the car holder 26 coupled to the brake body 28 and the elevator car 14 coupled to the car holder 26 are braked.

[0051] In the intended arrangement of the braking device 24, the car mount 26 is arranged on the elevator car 14 in the elevator shaft 12 such that the frictional force between the braking unit 30 and the corresponding guide rail 16 can be generated by means of the braking unit 30. The intended arrangement can also refer to the orientation of the elevator car 14. In particular, in the intended arrangement of the elevator car 14, a floor of the elevator car 14 is at the bottom and a roof of the elevator car 14 is at the top (as shown in Figure 1). Optionally, in the intended arrangement, the braking device 24 can be arranged below the elevator car 14.The intended arrangement of the braking device 24 can also refer to an orientation of the braking device 24, wherein the braking device 24 can, for example, be arranged as intended when the load measuring pin 32, in particular a longitudinal axis 78 of the load measuring pin 32 (see Figure 4), extends in the horizontal direction.

[0052] The brake unit 30 can, for example, be a mechanical and / or hydraulic brake. The brake unit 30 can, for example, have one, two, or more pairs of brake shoes (not shown). When the brake device 24 is arranged as intended, the corresponding guide rail 16 can run between the brake shoes. Optionally, the brake device 24 can have brake pads (not shown) that are arranged on the brake shoes such that the brake pads face the corresponding guide rail 16. The brake shoes and, if applicable, the brake pads can be designed and arranged such that, outside of the braking process, there is only very little or no physical contact between the brake shoes or the brake pads and the corresponding guide rail 16, and that during the braking process, the brake shoes or the brake pads touch the guide rail 16 and thereby generate the frictional force required for the braking process.

[0053] The brake unit 30 can, for example, have one, two or more springs 56, in particular C-shaped springs, for each pair of brake shoes. The springs 56 can be arranged on the brake body 28. The springs 56 can be pretensioned such that the springs 56 press the corresponding brake shoes towards the corresponding guide rail 16. The brake unit 30 can, for example, have a mechanically and / or hydraulically actuated lifting piston (not shown) for each spring 56, which is designed to press the brake shoes away from the corresponding guide rail 16 against the spring force of the corresponding spring 56. In this way, it can be ensured that in the event of a power failure and / or malfunction of the hydraulic system, in whichIn this case, the lifting piston cannot counteract the spring force, preventing the elevator car 14 from falling uncontrollably, since the brake shoes automatically initiate the braking process due to the spring force of the springs 56. If the lifting piston is hydraulically actuated, the necessary hydraulic fluid can be supplied to the lifting piston via a hydraulic connection 58.

[0054] The brake body 28 can have a first load-measuring pin receptacle 34. At least one longitudinal section 46 of the load-measuring pin 32 can be arranged in the first load-measuring pin receptacle 34. The first load-measuring pin receptacle 34 can be designed such that, when the braking device 24 is arranged as intended, the load-measuring pin 32 is positively secured in the first load-measuring pin receptacle 34 in a vertical direction and is displaceable in the horizontal direction relative to the first load-measuring pin receptacle 34. The first load-measuring pin receptacle 34 can serve as a bearing for the load-measuring pin 32. The first load-measuring pin receptacle 34 can, for example, have a first eyelet 36. When the braking device 24 is arranged as intended, a central axis of the first eyelet 36 can run horizontally.The first eyelet 36 can be configured with a clearance fit with the load-measuring pin 32, so that the load-measuring pin 32 can be arranged in the first eyelet 36 and can be rotated in the first eyelet 36 relative to the first eyelet 36. The fact that the load-measuring pin 32 is arranged in the first load-measuring pin receptacle 34 so as to be displaceable in the horizontal direction relative to the first load-measuring pin receptacle 34 enables the elevator car 14 to be movable in the horizontal direction relative to the braking device 24. For example, the load measuring pin 32 and the first load measuring pin holder 34 can be designed such that the elevator car 14 can be moved in the horizontal direction relative to the corresponding guide rail 16 within a range of ± 10 mm, for example within a range of ± 5 mm, for example within a range of ± 2 mm.

[0055] The first load-measuring pin receptacle 34 can be configured such that the brake body 28 is rotatable about the load-measuring pin 32 relative to the cabin mount 26. For example, the longitudinal axis 78 of the load-measuring pin 32 can be a rotation axis about which the brake body 28 is rotatable relative to the cabin mount 26.

[0056] The cabin mount 26 can have a second load-measuring pin receptacle 38. The second load-measuring pin receptacle 38 can be configured such that, when the braking device 24 is arranged as intended, the load-measuring pin 32 is positively secured in the second load-measuring pin receptacle 38 in the vertical direction and is displaceable in the horizontal direction relative to the second load-measuring pin receptacle 38. The second load-measuring pin receptacle 38 can, for example, have two second eyelets 40 that are arranged opposite one another and concentrically to one another, wherein the center axes of the second eyelets 40 can run horizontally and parallel to one another, for example, can lie on top of one another. The second eyelets 40 may be formed with a clearance fit to the load measuring pin 32 so that the load measuring pin 32 can be arranged in the second eyelets 40 and can be rotated in the second eyelets 40 relative to the second eyelets 40.Alternatively, two first eyelets 36 can be arranged on the brake body 28 and / or only a second eyelet 40 on the car mount 26. The second load-measuring pin receptacle 38 can be designed such that the brake body 28 can be rotated about the load-measuring pin 32 relative to the car mount 26. For example, the longitudinal axis 78 of the load-measuring pin 32 can be the axis of rotation about which the brake body 28 can be rotated relative to the car mount 26. When the braking device 24 is arranged as intended, the car mount 26 can be arranged on a first vertical end section 47 of the brake body 28. The braking device 24 can have a bearing arrangement 42 arranged on a second vertical end section 49 of the brake body 28. The second vertical end section 49 faces away from the first vertical end section 47.The bearing assembly 42 can be fixed relative to the elevator car 14 and movable in the vertical direction relative to the brake body 28. The bearing assembly 42 can be coupled to the elevator car 14 such that it is arranged directly on the elevator car 14 and contacts the elevator car 14. If the elevator car 14 is arranged in the catch frame 15, the bearing assembly 42 can be arranged on the catch frame 15, can contact the catch frame 15, and can be mechanically coupled to the elevator car 14 indirectly via the catch frame 15.

[0057] According to one embodiment, the bearing assembly 42 has a vertical piston 44. When the brake device 24 is arranged as intended, the vertical piston 44 extends into a recess 45 in the brake body 28 that extends in the vertical direction. The vertical piston 44 can thus extend in the vertical direction. The vertical piston 28 can be arranged in the recess 45 such that it is movable in the vertical direction relative to the brake body 28. For example, the vertical piston 44 can be designed with a clearance fit with the recess 45.

[0058] In particular, a longitudinal section 46 of the vertical piston 44 can be arranged in the recess 45. A third eyelet 48 can be formed at an elongated end of the longitudinal section 46. The bearing arrangement 42 can have a pin 50 that is guided through the third eyelet 48, that is movable relative to the third eyelet 48, and that is mechanically coupled to the elevator car 14 outside the third eyelet 48. The third eyelet 48 can, for example, be designed such that the pin 50 is aligned horizontally when it is arranged in the third eyelet 48. The third eyelet 48 and the pin 50 can be designed with a clearance fit relative to one another, whereby the mobility of the pin 50 relative to the third eyelet 48 can be ensured. The fact that the pin 50 is movable relative to the third eyelet 48 can mean, for example, that the third eyelet 48 can slide along the pin 50 and / or the third eyelet 48 can be rotated about the pin 50.For example, the pin 50 in the third eyelet 48 can be arranged so as to be displaceable in the horizontal direction relative to the third eyelet 48. For example, the pin 50 and the third eyelet 48 can be configured such that the elevator car 14 can be moved horizontally relative to the corresponding guide rail 16 within a range of ± 10 mm, for example within a range of ± 5 mm, for example within a range of ± 2 mm. The pin 50 can be arranged on a brake bracket 52, which can represent at least part of the mechanical coupling between the bearing assembly 42 and the elevator car 14. The brake bracket 52 can be coupled to the pin 50 by means of a connecting element 54. For example, the pin 50 can be held by the connecting element 54. The horizontal mobility of the third eyelet 48 relative to the pin 50 enables a floating mounting of the brake body 28.

[0059] The bearing arrangement 42 can form a moment support for a braking torque occurring during the braking process and acting on the braking device 24. Without the bearing arrangement 42, the brake body 28 could swing inward at the bottom due to the upper bearing of the braking device 24 formed by the load-measuring pin 32 when the elevator car 14 is displaced and not braked. When the elevator car 14 is then braked, the brake body 28 could swing outward or inward due to the braking torque, depending on the direction of movement, if the bearing arrangement 42 were not present. However, the bearing arrangement 42 should not absorb any force acting in the vertical direction, as this would relieve the load-measuring pin 32 and thereby falsify the measurement described below. This is ensured by the vertical piston 44 of the bearing arrangement 42, which is movable relative to the brake body 28.

[0060] The braking device 24 can have a guide element 60. The guide element 60 is arranged on the brake body 28. The guide element 60 is designed to guide the braking device 24 on the corresponding guide rail 16 during the displacement of the elevator car 14. The guide element 60 can have one, two, or more pairs of guide rollers 62. The guide rollers 62 are rotatably arranged on the brake body 28. When the braking device 24 is arranged as intended, the guide rail 26 is arranged between the guide rollers 62. The guide rollers 62 are designed and arranged such that the axes of rotation of the guide rollers 62 are parallel to one another and that rolling surfaces 65 of the guide rollers 62 face the corresponding guide rail 16 and roll along it when the braking device 24 is moved relative to the guide rail 16.

[0061] If the car assembly 13 has the catch frame 15 in which the elevator car 14 is arranged, the braking device 24 can be mechanically coupled to the catch frame 15, in particular directly, in particular such that at least one component of the braking device 24 is arranged on the catch frame 15 and touches it. The braking device 24 can thus be directly mechanically coupled to the elevator car 14 and to the catch frame 15. In particular, the braking device 24 can be mechanically coupled to the elevator car 14 by means of the car mount 26 and to the catch frame 15 by means of the bearing assembly 42. In particular, the car mount 26 can be arranged directly on the elevator car 14 and / or touch it, and the bearing assembly 42 can be arranged directly on the catch frame 15 and / or touch it.

[0062] Fig. 4 shows a partially sectioned side detail view of the braking device 24 according to Figure 2. Figure 4 shows that at least part of an elongated section, for example, part of a first axial section 72 and part of a second axial section 74, of the load measuring pin 32 can be arranged in the second load measuring pin receptacle 38. Furthermore, Figure 4 shows that at least part of an elongated section, for example, part of a third axial section 76, of the load measuring pin 32 can be arranged in the first load measuring pin receptacle 34.

[0063] Furthermore, Figure 4 shows that the load-measuring pin 32 has a longitudinal axis 78. The load-measuring pin 32 can be arranged such that the longitudinal axis 78 extends in the horizontal direction. The load-measuring pin 32 can be designed to be substantially rotationally symmetrical to the longitudinal axis 78. In this case, the longitudinal axis 78 can correspond to an axis of symmetry of the load-measuring pin 32. The load-measuring pin 32 can, for example, be designed to be substantially cylindrical. The load-measuring pin 32 can have a cavity 68. The cavity 68 can extend at least partially through the load-measuring pin 32 parallel to the longitudinal axis 78.

[0064] The load measuring pin 32 can have a strain gauge 70, which serves as a sensor for detecting the force acting on the load measuring pin 32 in the vertical direction. The load measuring pin 32 and the strain gauge 70 can be arranged such that a force acting between the car mount 26 and the guide element 60 in a direction parallel to the guide rail 16 during the braking process causes the load measuring pin 32 to bend and thus the strain gauge 70 to stretch. The strain gauge 70 can be arranged in the cavity 68.

[0065] The strain gauge 70 is designed such that when the strain gauge 70 is stretched, its electrical resistance changes. The stretching can occur as a result of the bending of the load measuring pin 32, which results from the force acting on the load measuring pin in the vertical direction. The fact that the load measuring pin 32 and the strain gauge 70 are arranged such that the force acting between the car mount 26 and the guide element 60 in a direction parallel to the guide rail 16 during the braking process causes a bending of the load measuring pin 32 and thus an stretching of the strain gauge 70 can, in the most general case, mean that when the braking device 24 is arranged as intended, the longitudinal axis 78 of the load measuring pin 32 or of the strain gauge 70 extends at least partially in the horizontal direction.Ideally, this can mean that the longitudinal axis 78 and the strain gauge 70 extend horizontally and thus perpendicular to the force acting in the vertical direction. In this case, the deflection of the load pin 32 and the resulting elongation of the strain gauge 70 are maximized for a given force, so that a very good signal-to-noise ratio can be achieved and the force can be determined very precisely.

[0066] The load measuring pin 32 may include an electronic component 80. The electronic component 80 may be arranged in or on the load measuring pin 32. Alternatively, the electronic component 80 may be arranged independently of the load measuring pin 32. The electronic component 80 is connected to the - TI -

[0067] Strain gauges 80 are electrically connected, for example by means of two electrical lines 82. The electronic component 80 can, for example, have or be a full bridge. The electronic component 80 can be communicatively coupled to an evaluation unit external to the braking device 24, for example by cable via a component connection 66 that is electrically coupled to the electronic component 80 and to the external evaluation unit. The external evaluation unit can, for example, be a component of the elevator control 22 or be included therein. Alternatively, the evaluation unit can be arranged on or in the elevator car 14 and / or can be a component of a car control (not shown) of the elevator system 10. Alternatively, the evaluation unit can be a component of the braking device 24.

[0068] The electronic component 80 is designed to determine, in particular to detect, the electrical resistance of the strain gauge 70. For example, the electronic component 80 can be designed to apply a voltage to the strain gauge 70 and to detect a current flowing through the strain gauge 70 due to the applied voltage, and to determine the resistance depending on the applied voltage and the detected current. To apply the voltage, the electronic component 80 can be connected to a power source (not shown), for example, a battery or a power grid. Depending on the resistance of the strain gauge 70, the electronic component 80 can generate an output signal.The output signal of the electronic component 80 is representative of the electrical resistance of the strain gauge 70, thus of the extent of the strain gauge 70's elongation, and thus of the force acting on the load measuring pin 32 due to the braking process. Depending on this force, the load currently being transported by the elevator car 14 can then be determined.

[0069] Thus, the load measuring bolt 32 with the strain gauge 70 and the electronic component 80 serve as the load measuring device 33 of the braking device 24.

[0070] Determining the load as a function of force is generally known, for example, from the prior art cited at the beginning. Therefore, the basic procedure will only be briefly discussed below: The output signal of the electronic component 80 can be received by the evaluation unit. The evaluation unit can be configured to determine the force acting on the load measuring pin 32 due to the braking process, depending on the output signal of the electronic component 80. In particular, the output signal is representative of the elongation of the strain gauge 70. The elongation of the strain gauge 70 occurs due to the bending of the load measuring pin 32 as a result of the force acting on it.Since the material and, in particular, the bending properties of the load-measuring pin 32 are known, the force can be determined based on the bending of the load-measuring pin 32, which is representative of the force, and, in particular, based on the corresponding elongation of the strain gauge 70, for which the output signal is representative. Since the weight of the empty elevator car 14 and, if applicable, the weight of the counterweight coupled to the elevator car 14 via the support means 18 are known, the weight of the load currently being transported by the elevator car 14 can then be determined based on the determined force. The load can include people and / or goods. The force can act in different directions depending on the load.For example, if the counterweight is selected such that the empty elevator car 14 is lighter than the counterweight and the fully loaded elevator car 14 is heavier than the counterweight, the counterweight will pull the empty elevator car 14 upward, so that the force on the load pin 32 acts upward, and the fully loaded elevator car 14 will pull the counterweight upward and push the car mount 26 downward, so that the force acts downward. For example, the counterweight can be selected such that it corresponds to the total weight of the empty elevator car and the weight of half the maximum load.

[0071] Should the load to be transported change during a stop of the elevator car 14, for example due to one or more passengers entering or leaving the elevator car 14, then, provided the current load is known, the support means 18 can be tightened or loosened depending on the determined load in such a way that no jerky movement of the elevator car 14 occurs when the brake is released.

[0072] Finally, it should be noted that terms such as "having," "comprising," etc., do not exclude other elements or steps, and terms such as "a" or "an" do not exclude a plurality. Furthermore, it should be noted that features or steps described with reference to one of the above embodiments may also be used in combination with other features or steps of other embodiments described above. Reference signs in the claims are not to be considered as limitations.

Claims

Patent claims 1. Braking device (24) with load measuring device (33) for an elevator system (10), the elevator system (10) comprising an elevator shaft (12), an elevator car (14) which is arranged displaceably in the elevator shaft (12), and at least one guide rail (16) which is fixedly arranged in the elevator shaft (12) and which is designed to guide the elevator car (14) during displacement thereof, the braking device (24) comprising: a car holder (26) for fastening the braking device (24) to the elevator car (14); a brake body (28) which is mechanically coupled to the car holder (26);a brake unit (30) which is arranged on the brake body (28) and which is designed to be brought into physical contact with the guide rail (16) when the brake device (24) is arranged as intended on the elevator car (14) and during a braking operation of the elevator system (10) and to generate such a high frictional force between the guide rail (16) and the brake unit (30) that the brake unit (30) and the elevator car (14) coupled to the brake unit (30) are braked;a load measuring bolt (32) by means of which the car holder (26) is mechanically coupled to the brake body (28) and which has a strain gauge (70), wherein the load measuring bolt (32) and the strain gauge (70) are arranged such that a force acting between the car holder (26) and the brake body (28) in a direction parallel to the guide rail (16) during the braking process causes a bending of the load measuring bolt (32) and thus an elongation of the strain gauge (70);and an electronic component (80) which is electrically coupled to the strain gauge (70) and which is designed to generate an output signal depending on the strain of the strain gauge (70), wherein the output signal is representative of the force and wherein a load which is currently being carried by the elevator car (14) can be determined depending on the force, so that the load measuring bolt (32) and the electronic component (80) can be used as the load measuring device (33); 2. Braking device (24) according to claim 1, wherein the load measuring pin (32) has a longitudinal axis (78), the load measuring pin (32) has a cavity (68) which extends parallel to the longitudinal axis (78) at least partially through the load measuring pin (32), and the strain gauge (70) is arranged in the cavity (68).

3. Braking device (24) according to claim 2, wherein the load measuring pin (32) is arranged such that the longitudinal axis (78) extends in the horizontal direction.

4. Braking device (24) according to one of the preceding claims, wherein the brake body (28) has a first load-measuring pin receptacle (34) in which at least one axial section (76) of the load-measuring pin (32) is arranged and which is designed such that, when the braking device (24) is arranged as intended, the load-measuring pin (32) is positively secured in the first load-measuring pin receptacle (34) in the vertical direction and is displaceable in the horizontal direction relative to the first load-measuring pin receptacle (34).

5. Braking device (24) according to claim 4, wherein the first load measuring pin receptacle (34) is designed such that the brake body (28) is rotatable about the load measuring pin (32) relative to the cabin holder (26).

6. Braking device (24) according to one of the preceding claims, wherein the cabin holder (26) has a second load-measuring pin receptacle (38) in which at least one axial section (72, 74) of the load-measuring pin (32) is arranged and which is designed such that, when the braking device (24) is arranged as intended, the load-measuring pin (32) is positively secured in the second load-measuring pin receptacle (38) in the vertical direction and is displaceable in the horizontal direction relative to the second load-measuring pin receptacle (38).

7. Braking device (24) according to claim 6, wherein the second load measuring pin receptacle (38) is designed such that the brake body (28) is rotatable about the load measuring pin (32) relative to the cabin holder (26).

8. Braking device (24) according to one of the preceding claims, wherein the car holder (26) is arranged on a first vertical end section (47) of the brake body (28) in the intended arrangement of the braking device (24), the braking device (24) further comprising: a bearing arrangement (42) which is arranged on a second vertical end section (49) of the brake body (28), which is facing away from the first vertical end section (47), which is fixed relative to the elevator car (14) and which is movable in the vertical direction relative to the brake body (28).

9. Braking device (24) according to claim 8, the bearing arrangement (42) comprising: a vertical piston (44) which is in a position which, during the intended Arrangement of the braking device (24) in the recess (45) of the brake body (28) extending in the vertical direction is arranged such that the vertical piston (44) extends in the vertical direction and that the vertical piston (44) is movable in the vertical direction relative to the brake body (28).

10. Braking device (24) according to claim 9, wherein a longitudinal section (46) of the vertical piston (44) is arranged in the recess (45), a third eyelet (48) is formed at an elongated end of the longitudinal section (46), the bearing arrangement (42) has a pin (50) which is guided through the third eyelet (48), which is movable relative to the third eyelet (48), and which is mechanically coupled to the elevator car (14) outside the third eyelet (48).

11. Braking device (24) according to one of the preceding claims, comprising: a guide element (60) which is arranged on the brake body (28) and which is designed to guide the braking device (24) on the guide rail (16) during the displacement of the elevator car (14).

12. Braking device (24) according to claim 11, the guide element (60) comprising: at least one pair of guide rollers (62) which are rotatably arranged on the brake body (28) and between which the guide rail (16) is arranged when the braking device (24) is arranged as intended, wherein the guide rollers (62) are designed and arranged such that axes of rotation of the guide rollers (62) are parallel to one another and that rolling surfaces (65) of the guide rollers (62) face the guide rail (16) and roll along it when the braking device (24) is moved relative to the guide rail (16).

13. A car assembly (13) for an elevator system (10) having an elevator shaft (12), the car assembly (13) comprising: an elevator car (14); and at least one braking device (24) according to one of the preceding claims, which is arranged on the elevator car (14).

14. Cabin arrangement (13) according to claim 13, comprising a catch frame (15) in which the elevator car (14) is arranged, wherein the braking device (24) is mechanically coupled to the catch frame (15).

15. Elevator system (10), comprising: an elevator shaft (12); and a car arrangement (13) according to claim 13 or 14.

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